High pressure pump

ABSTRACT

A high pressure pump comprising a fluid end mechanically coupled to a power end. The power end is modular and comprises a crankshaft section, a crosshead section, and a connector section coupled together by a first set of stay rods. The fluid end comprises a plurality of fluid end sections positioned in a side-by-side relationship. Each of the plurality of fluid end sections are attached to the power end using a plurality of second set of stay rods.

RELATED APPLICATIONS

This application claims priority to U.S. patent application Ser. No.16/951,895 authored by Nowell et al. and filed on Nov. 18, 2020, andalso claims the benefit of the following provisional patentapplications: Ser. No. 62/936,789, authored by Thomas et al. and filedon Nov. 18, 2019; Ser. No. 62/940,513, authored by Thomas et al. andfiled on Nov. 26, 2019; Ser. No. 62/953,763, authored by Thomas et al.and filed on Dec. 26, 2019; Ser. No. 62/957,489, authored by Foster etal. and filed on Jan. 6, 2020; Ser. No. 62/959,570, authored by Thomaset al. and filed on Jan. 10, 2020; Ser. No. 62/960,194, authored byFoster et al. and filed on Jan. 13, 2020; Ser. No. 62/960,366, authoredby Foster et al. and filed on Jan. 13, 2020; Ser. No. 62/968,634,authored by Foster et al. and filed on Jan. 31, 2020; Ser. No.62/990,817, authored by Thomas et al. and filed on Mar. 17, 2020; Ser.No. 63/008,036, authored by Thomas et al. and filed on Apr. 10, 2020;Ser. No. 63/018,021, authored by Thomas et al. and filed Apr. 30, 2020;Ser. No. 63/019,789, authored by Thomas et al. and filed on May 4, 2020;Ser. No. 63/027,584, authored by Thomas et al. and filed on May 20,2020; Ser. No. 63/033,244, authored by Thomas et al. and filed Jun. 2,2020; Ser. No. 63/040,086, authored by Thomas et al. and filed on Jun.17, 2020; Ser. No. 63/046,826, authored by Thomas et al. and filed onJul. 1, 2020; Ser. No. 63/053,797, authored by Thomas et al. and filedon Jul. 20, 2020; Ser. No. 63/076,587, authored by Thomas et al. andfiled on Sep. 10, 2020; and Ser. No. 63/089,882, authored by Thomas etal. and filed on Oct. 9, 2020. The entire contents of all of the abovelisted provisional patent applications are incorporated herein byreference.

BACKGROUND

Various industrial applications may require the delivery of high volumesof highly pressurized fluids. For example, hydraulic fracturing(commonly referred to as “fracking”) is a well stimulation techniqueused in oil and gas production, in which highly pressurized fluid isinjected into a cased wellbore. As shown for example in FIG. 1 , thepressured fluid flows through perforations 10 in a casing 12 and createsfractures 14 in deep rock formations 16. Pressurized fluid is deliveredto the casing 12 through a wellhead 18 supported on the ground surface20. Sand or other small particles (commonly referred to as “proppants”)are normally delivered with the fluid into the rock formations 16. Theproppants help hold the fractures 14 open after the fluid is withdrawn.The resulting fractures 14 facilitate the extraction of oil, gas, brine,or other fluid trapped within the rock formations 16.

Fluid ends are devices used in conjunction with a power source topressurize the fluid used during hydraulic fracturing operations. Asingle fracking operation may require the use of two or more fluid endsat one time. For example, six fluid ends 22 are shown operating at awellsite 24 in FIG. 2 . Each of the fluid ends 22 is attached to a powerend 26 in a one-to-one relationship. The power end 26 serves as anengine or motor for the fluid end 22. Together, the fluid end 22 andpower end 26 function as a hydraulic pump.

Continuing with FIG. 2 , a single fluid end 22 and its correspondingpower end 26 are typically positioned on a truck bed 28 at the wellsite24 so that they may be easily moved, as needed. The fluid and proppantmixture to be pressurized is normally held in large tanks 30 at thewellsite 24. An intake piping system 32 delivers the fluid and proppantmixture from the tanks 30 to each fluid end 22. A discharge pipingsystem 33 transfers the pressurized fluid from each fluid end 22 to thewellhead 18, where it is delivered into the casing 12 shown in FIG. 1 .

Fluid ends operate under notoriously extreme conditions, enduring thesame pressures, vibrations, and abrasives that are needed to fracturethe deep rock formations shown in FIG. 1 . Fluid ends may operate atpressures of 5,000-15,000 pounds per square inch (psi) or greater. Fluidused in hydraulic fracturing operations is typically pumped through thefluid end at a pressure of at least 8,000 psi, and more typicallybetween 10,000 and 15,000 psi. However, the pressure may reach up to22,500 psi. The power end used with the fluid end typically has a poweroutput of at least 2,250 horsepower during hydraulic fracturingoperations. A single fluid end typically produces a fluid volume ofabout 400 gallons, or 10 barrels, per minute during a frackingoperation. A single fluid end may operate in flow ranges from 170 to 630gallons per minute, or approximately 4 to 15 barrels per minute. When aplurality of fluid ends are used together, the fluid ends collectivelydeliver about 4,200 gallons per minute or 100 barrels per minute to thewellbore.

In contrast, mud pumps known in the art typically operate at a pressureof less than 8,000 psi. Mud pumps are used to deliver drilling mud to arotating drill bit within the wellbore during drilling operations. Thus,the drilling mud does not need to have as high of fluid pressure asfracking fluid. A fluid end does not pump drilling mud. A power end usedwith mud pumps typically has a power output of less than 2,250horsepower. Mud pumps generally produce a fluid volume of about 150-600gallons per minute, depending on the size of pump used.

In further contrast, a fluid jetting pump known in the art typicallyoperates at pressures of 30,000-90,000 psi. Jet pumps are used todeliver a highly concentrated stream of fluid to a desired area. Jetpumps typically deliver fluid through a wand. Fluid ends do not deliverfluid through a wand. Unlike fluid ends, jet pumps are not used inconcert with a plurality of other jet pumps. Rather, only a single jetpump is used to pressurize fluid. A power end used with a jet pumptypically has a power output of about 1,000 horsepower. Jet pumpsgenerally produce a fluid volume of about 10 gallons per minute.

High operational pressures may cause a fluid end to expand or crack.Such a structural failure may lead to fluid leakage, which leaves thefluid end unable to produce and maintain adequate fluid pressures.Moreover, if proppants are included in the pressurized fluid, thoseproppants may cause erosion at weak points within the fluid end,resulting in additional failures.

It is not uncommon for conventional fluid ends to experience failureafter only several hundred operating hours. Yet, a single frackingoperation may require as many as fifty (50) hours of fluid endoperation. Thus, a traditional fluid end may require replacement afteruse on as few as two fracking jobs.

During operation of a hydraulic pump, the power end is not exposed tothe same corrosive and abrasive fluids that move through the fluid end.Thus, power ends typically have much longer lifespans than fluid ends. Atypical power end may service five or more different fluid ends duringits lifespan. However, as described below, common failure points arealso found in traditional power ends.

With reference to FIG. 3 , a traditional power end 34 is shown. Thepower end 34 comprises a housing 36 having a mounting plate 38 formed onits front end 40. The housing 36 is traditionally a one-piece framefabricated from steel plate and/or casting to provide a structure tomount a crankshaft and drive apparatus. The housing 36 is very heavy dueto the size of the material needed to withstand the forces appliedduring operation and because of the large mount areas needed to attachthe various components.

Continuing with FIG. 3 , a plurality of stay rods 42 are attached to andproject from the mounting plate 38. The stay rods 42 are typicallytorqued into threaded holes formed in the mounting plate 38. A fluidend, such as a fluid end 46, attaches to the projecting ends of the stayrods 42, such that the power end 34 supports the weight of the fluidend.

Traditional power ends, like the power end 34, often fail at themounting plate 38. During operation, high areas of stress concentrationare produced at the threaded holes formed in the mounting plate 38 forreceiving the stay rods 42. Typical failures include breaking of thethreads or areas of the mounting plate 38 adjacent the threaded holes,and weld failures. All of these failures require significant repair to,or complete replacement of, the power end.

Continuing with FIG. 3 , a plurality of pony rods 44 are disposed atleast partially within the power end 34 and project from openings formedin the mounting plate 38. Each of the pony rods 44 is attached to acrank shaft installed within the housing 36. Rotation of the crank shaftpowers reciprocal motion of the pony rods 44 relative to the mountingplate 38. Other common failures in traditional power ends occur due topoor lubrication of the moving parts.

It is known in the art to lubricate the main bearings and connecting rodbearings by forcing pressurized lubricant through a center bore andintersecting cross bores in the crankshaft. It is also known in the artto lubricate the wrist pin, connecting rod end, thrust seat andcrosshead by forcing pressurized lubricant into the crosshead bore andintersecting cross bores through the crosshead, thrust seat, andcrosshead end of the connecting rod. The problem is that the entirelubrication system is a single system. One lubrication pump pressurizesa manifold to which all lubrication circuits are attached.

During operation components wear and clearances between the componentsincrease. This increase in the clearances reduces the amount ofresistance to lubricant flow resulting in higher lubricant flow in thatarea. While higher lubricant flow results in reduced wear in thatcircuit, the other circuits will experience reduced flow and higherwear. The reduced lubricant flow will accelerate the wear in anotherarea increasing clearances until it receives enough lubricant to stoperoding. This alternating wear and lubrication cycle repeats causinguneven and accelerated wear in the components of the power end reducingmaintenance intervals.

In order to reduce, mitigate, or eliminate the failures listed above,the inventors propose a novel power end assembly with modularconstruction, as described below. Such modular construction also reducesthe physical dimensions and weight

Continuing with FIG. 3 , the fluid end 46 comprises a single housing 48having a flange 50 machined therein. The flange 50 provides a connectionpoint for the plurality of stay rods 42. The stay rods 42 rigidlyinterconnect the power end 34 and the fluid end 46. When connected, thefluid end 46 is suspended in offset relationship to the power end 34.

A plurality of plungers 52 are disposed within the fluid end 46 andproject from openings formed in the flange 50. The plungers 52 and ponyrods 44 are arranged in a one-to-one relationship, with each plunger 52aligned with and connected to a corresponding one of the pony rods 44.Reciprocation of each pony rod 44 causes its connected plunger 52 toreciprocate within the fluid end 46. In operation, reciprocation of theplungers 52 pressurizes fluid within the fluid end 46. The reciprocationcycle of each plunger 52 is differently phased from that of eachadjacent plunger 52.

With reference to FIG. 5 , the interior of the fluid end 46 includes aplurality of longitudinally spaced bore pairs. Each bore pair includes avertical bore 56 and an intersecting horizontal bore 58. The zone ofintersection between the paired bores defines an internal chamber 60.Each plunger 52 extends through a horizontal bore 58 and into itsassociated internal chamber 60. The plungers 52 and horizontal bores 58are arranged in a one-to-one relationship.

Each horizontal bore 58 is sized to receive a plurality of packing seals64. The seals 64 are configured to surround the installed plunger 52 andprevent high-pressure fluid from passing around the plunger 52 duringoperation. The packing seals 64 are maintained within the bore 58 by aretainer 65. The retainer 65 has external threads 63 that mate withinternal threads 67 formed in the walls surrounding the bore 58. In sometraditional fluid ends, the packing seals 64 are installed within aremovable stuffing box sleeve that is installed within the horizontalbore.

Each vertical bore 56 interconnects opposing top and bottom surfaces 66and 68 of the fluid end 46. Each horizontal bore 58 interconnectsopposing front and rear surfaces 70 and 72 of the fluid end 46. Adischarge plug 74 seals each opening of each vertical bore 56 on the topsurface 66 of the fluid end 46. Likewise, a suction plug 76 seals eachopening of each horizontal bore 58 on the front surface 70 of the fluidend 46.

Each of the plugs 74 and 76 features a generally cylindrical body. Anannular seal 77 is installed within a recess formed in an outer surfaceof that body, and blocks passage of high pressure fluid. The dischargeand suction plugs 74 and 76 are retained within their correspondingbores 56 and 58 by a retainer 78, shown in FIGS. 3, 5, and 6 . Theretainer 78 has a cylindrical body having external threads 79 formed inits outer surface. The external threads 79 mate with internal threads 81formed in the walls surrounding the bore 56 or 58 between the installedplug 74 or 76 and the surface 66 or 70 of the fluid end 46.

As shown in FIG. 3 , a single manifold 80 is attached to the fluid end46. The manifold 80 is also connected to an intake piping system, of thetype shown in FIG. 2 . Fluid to be pressurized is drawn from the intakepiping system into the manifold 80, which directs the fluid into each ofthe vertical bores 56, by way of openings (not shown) in the bottomsurface 68.

When a plunger 52 is retracted, fluid is drawn into each internalchamber 60 from the manifold 80. When a plunger 52 is extended, fluidwithin each internal chamber 60 is pressurized and forced towards adischarge conduit 82. Pressurized fluid exits the fluid end 46 throughone or more discharge openings 84, shown in FIGS. 3-5 . The dischargeopenings 84 are in fluid communication with the discharge conduit 82.The discharge openings 84 are attached to a discharge piping system, ofthe type shown in FIG. 2 .

A pair of valves 86 and 88 are installed within each vertical bore 56,on opposite sides of the internal chamber 60. The valve 86 preventsbackflow in the direction of the manifold 80, while the valve 88prevents backflow in the direction of the internal chamber 60. Thevalves 86 and 88 each comprise a valve body 87 that seals against avalve seat 89.

Traditional fluid ends are normally machined from high strength alloysteel. Such material can corrode quickly, leading to fatigue cracks.Fatigue cracks occur because corrosion of the metal decreases themetal's fatigue strength—the amount of loading cycles that can beapplied to a metal before it fails. Such cracking can allow leakage thatprevents a fluid end from achieving and maintaining adequate pressures.Once such leakage occurs, fluid end repair or replacement becomesnecessary.

Fatigue cracks in fluid ends are commonly found in areas that experiencehigh stress. For example, with reference to the fluid end 46 shown inFIG. 5 , fatigue cracks are common at a corner 90 formed in the interiorof the fluid end 46 by the intersection of the walls surrounding thehorizontal bore 58 with the walls surrounding the vertical bore 56. Aplurality of the corners 90 surround each internal chamber 60. Becausefluid is pressurized within each internal chamber 60, the corners 90typically experience the highest amount of stress during operation,leading to fatigue cracks. Fatigue cracks are also common at the neckthat connects the flange 50 and the housing 48. Specifically, fatiguecracks tend to form at an area 92 where the neck joins the housing 48,as shown for example in FIGS. 4 and 5 .

For the above reasons, there is a need in the industry for a fluid endconfigured to avoid or significantly delay the structures or conditionsthat cause wear or failures within a fluid end.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is an illustration of the underground environment of a hydraulicfracturing operation.

FIG. 2 illustrates above-ground equipment used in a hydraulic fracturingoperation.

FIG. 3 is a left side perspective view of a traditional fluid endattached to a traditional power end.

FIG. 4 is a top plan view of the fluid end shown in FIG. 3 .

FIG. 5 is a sectional view of the fluid end shown in FIG. 4 , takenalong line A-A.

FIG. 6 is a front perspective view of one embodiment of a high pressurepump.

FIG. 6A is a front perspective view of a fluid end. A plurality of stayrods are attached to the fluid end.

FIG. 7 is a rear perspective view of the fluid end shown in FIG. 6 , butthe plurality of stay rods have been removed.

FIG. 7A is a side elevational view of the fluid end shown in FIG. 6 ,but with another embodiment of intake and discharge manifolds.

FIG. 7B is a front perspective view of the fluid end shown in FIG. 7A.

FIG. 8 is a front perspective view of one of the fluid end sectionsmaking up the fluid end shown in FIG. 6 .

FIG. 9 is a cross-sectional view of the fluid end section shown in FIG.8 , taken along line D-D.

FIG. 10 is a perspective view of a first surface of a connect plate usedwith the fluid end shown in FIG. 6 .

FIG. 11 is a perspective view of a second surface of the connect plateshown in FIG. 10 .

FIG. 12 is an elevational view of the first surface of the connect plateshown in FIG. 10 .

FIG. 13 is an elevational view of the second surface of the connectplate shown in FIG. 10 .

FIG. 14 is a perspective view of a second surface of a housing making upthe fluid end section shown in FIG. 8 .

FIG. 15 is an elevational view of the second surface of the housingshown in FIG. 14 .

FIG. 16 is a cross-sectional view of the fluid end and stay rods shownin FIG. 6 , taken along a plane that includes the line B-B.

FIG. 17 is a cross-sectional view of the fluid end and stay rods shownin FIG. 6 , taken along a plane that includes the line C-C.

FIG. 18 is a top plan view of the housing shown in FIG. 14 .

FIG. 19 is an enlarged view of area E shown in FIG. 9 .

FIG. 20 is the cross-sectional view of the fluid end section shown inFIG. 17 with the upper and lower intake manifolds shown attached to thehousing.

FIG. 21 is a rear perspective view of the fluid end section shown inFIG. 20 , but the plunger has been removed.

FIG. 22 is a top plan view of a stuffing box shown attached to thehousing in FIG. 20 .

FIG. 23 is a perspective view of a first surface of the stuffing boxshown in FIG. 22 .

FIG. 24 is an elevational view of the first surface of the stuffing boxshown in FIG. 22 .

FIG. 25 is a cross-sectional view of the stuffing box shown in FIG. 24 ,taken along line F-F.

FIG. 26 is a cross-sectional view of the stuffing box shown in FIG. 24 ,taken along line G-G.

FIG. 27 is a perspective view of a second surface of the stuffing boxshown in FIG. 22 .

FIG. 28 is an elevational view of the second surface of the stuffing boxshown in FIG. 22 .

FIG. 29 is a cross-sectional view of the stuffing box shown in FIG. 28 ,taken along line H-H.

FIG. 30 is a top plan view of a retainer shown attached to the stuffingbox in FIG. 20 .

FIG. 31 is a perspective view of a first surface of the retainer shownin FIG. 30 .

FIG. 32 is an elevational view of the first surface of the retainershown in FIG. 30 .

FIG. 33 is a cross-sectional view of the retainer shown in FIG. 32 ,taken along line I-I.

FIG. 34 is a cross-sectional view of the retainer shown in FIG. 36 ,taken along line J-J.

FIG. 35 is a perspective view of a second surface of the retainer shownin FIG. 30 .

FIG. 36 is an elevational view of the second surface of the retainershown in FIG. 30 .

FIG. 37 is a cross-sectional view of the retainer shown in FIG. 36 ,taken along line K-K.

FIG. 38 is a top plan view of a plunger packing shown installed withinthe stuffing box and retainer in FIG. 20 .

FIG. 39 is a perspective view of a first surface of the plunger packingshown in FIG. 38 .

FIG. 40 is an elevational view of the first surface of the plungerpacking shown in FIG. 38 .

FIG. 41 is a cross-sectional view of the plunger packing shown in FIG.40 , taken along line L-L.

FIG. 42 is a perspective exploded view of the plunger packing shown inFIG. 38 .

FIG. 43 is a top plan view of a packing nut shown installed within theretainer in FIG. 20 .

FIG. 44 is a perspective view of a first surface of the packing nutshown in FIG. 43 .

FIG. 45 is an elevational view of the first surface of the packing nutshown in FIG. 43 .

FIG. 46 is a cross-sectional view of the packing nut shown in FIG. 45 ,taken along line M-M.

FIG. 47 is a perspective view of a first surface of a retainer showninstalled within the housing in FIG. 20 .

FIG. 48 is an elevational view of the first surface of the retainershown in FIG. 47 .

FIG. 49 is a cross-sectional view of the retainer shown in FIG. 48 ,taken along line N-N.

FIG. 50 is the cross-sectional view shown in FIG. 9 , but the suctionvalve is spaced from the fluid routing plug.

FIG. 51 is the cross-sectional view shown in FIG. 50 , but the plungerhas extended into the housing, the suction valve is sealed against thefluid routing plug, and the discharge valve is spaced from the fluidrouting plug.

FIG. 52 is a perspective view of a second surface of a fluid routingplug shown installed within the fluid end section in FIG. 50 .

FIG. 53 is a perspective view of a first surface of the fluid routingplug shown in FIG. 52 .

FIG. 54 is an elevational view of the second surface of the fluidrouting plug shown in FIG. 52 .

FIG. 55 is a cross-sectional view of the fluid routing plug shown inFIG. 54 , taken along line O-O.

FIG. 56 is an elevational view of the first surface of the fluid routingplug shown in FIG. 52 .

FIG. 57 is a top plan view of the fluid routing plug shown in FIG. 52 .

FIG. 58 is a cross-sectional view of the fluid routing plug shown inFIG. 57 , taken along line P-P.

FIG. 59 is an enlarged view of area Q shown in FIG. 57 .

FIG. 60 is the top plan view of the fluid routing plug shown in FIG. 57, but the plug has been slightly rotated.

FIG. 61 is a cross-sectional view of the fluid routing plug shown inFIG. 60 , taken along line R-R.

FIG. 62 is a cross-sectional view of the fluid routing plug shown inFIG. 60 , taken along line S-S.

FIG. 63 is a cross-sectional view of the fluid routing plug shown inFIG. 60 , taken along line T-T.

FIG. 64 is an enlarged view of the fluid routing plug shown in FIG. 60 .

FIG. 65 is the cross-sectional view shown in FIG. 50 .

FIG. 66 is an enlarged view of area U shown in FIG. 65 .

FIG. 67 is an enlarged view of area V shown in FIG. 65 .

FIG. 68 is an enlarged view of area W shown in FIG. 65 .

FIG. 69 is an enlarged view of area X shown in FIG. 65 .

FIG. 70 is an enlarged view of area Y shown in FIG. 65 .

FIG. 71 is an enlarged view of area Z shown in FIG. 65 .

FIG. 72 is a top plan view of a suction valve shown installed within thehousing in FIG. 50 .

FIG. 73 is a perspective view of a second surface of the suction valveshown in FIG. 72 .

FIG. 74 is an elevational view of the second surface of the suctionvalve shown in FIG. 72 .

FIG. 75 is a perspective view of a first surface of the suction valveshown in FIG. 72 .

FIG. 76 is a cross-sectional view of the suction valve shown in FIG. 74, taken along line AA-AA.

FIG. 77 is a top plan view of a suction valve guide shown installedwithin the housing shown in FIG. 50 .

FIG. 78 is a perspective view of a first surface of the suction valveguide shown in FIG. 77 .

FIG. 79 is an elevation view of the first surface of the suction valveguide shown in FIG. 77 .

FIG. 80 is a cross-sectional view of the suction valve guide shown inFIG. 79 , taken along line AB-AB.

FIG. 81 is a perspective view of a second surface of the suction valveguide shown in FIG. 77 .

FIG. 82 is an elevational view of the second surface of the suctionvalve guide shown in FIG. 77 .

FIG. 83 is a perspective view of the suction valve guide shown in FIG.77 engaged with the suction valve shown in FIG. 72 . A spring is shownpositioned between the suction valve guide and the suction valve.

FIG. 84 is a top plan view of the suction valve guide, suction valve,and spring shown in FIG. 83 .

FIG. 85 is a top plan view of a discharge valve shown installed withinthe housing in FIG. 50 .

FIG. 86 is a perspective view of a second surface of the discharge valveshown in FIG. 85 .

FIG. 87 is an elevational view of the second surface of the dischargevalve shown in FIG. 85 .

FIG. 88 is a perspective view of a first surface of the discharge valveshown in FIG. 85 .

FIG. 89 is a cross-sectional view of the discharge valve shown in FIG.87 , taken along line AC-AC.

FIG. 90 is a top plan view of a discharge valve guide shown installedwithin the housing in FIG. 50 .

FIG. 91 is a perspective view of a first surface of the discharge valveguide shown in FIG. 90 .

FIG. 92 is an elevation view of the first surface of the discharge valveguide shown in FIG. 90 .

FIG. 93 is a cross-sectional view of the discharge valve guide shown inFIG. 92 , taken along line AD-AD.

FIG. 94 is a cross-sectional view of the discharge valve guide shown inFIG. 92 , taken along line AE-AE.

FIG. 95 is a perspective view of a second surface of the discharge valveguide shown in FIG. 90 .

FIG. 96 is a perspective cut-away view of a first surface of the fluidend section shown in FIG. 8 .

FIG. 97 is an enlarged view of area AF shown in FIG. 96 .

FIG. 98 is a perspective view of the discharge valve guide shown in FIG.90 engaged with the discharge valve shown in FIG. 85 . A spring is shownpositioned between the discharge valve guide and the discharge valve.

FIG. 99 is a top plan view of the discharge valve guide, dischargevalve, and spring shown in FIG. 98 .

FIG. 100 is the cross-sectional view of the fluid end section shown inFIG. 9 .

FIG. 100A is a perspective view of a second surface of anotherembodiment of a fluid routing plug.

FIG. 100B is a perspective view of a first surface of the fluid routingplug shown in FIG. 100A.

FIG. 100C is an elevational view of the second surface of the fluidrouting plug shown in FIG. 100A.

FIG. 100D is a cross-sectional view of the fluid routing plug shown inFIG. 100C, taken along line JA-JA.

FIG. 100E is a cross-sectional view of the fluid routing plug shown inFIG. 100C, taken along line JB-JB.

FIG. 100F is the cross-sectional view of the fluid end section shown inFIG. 9 , but the fluid routing plug from FIG. 100A is shown installedwithin the housing.

FIG. 100G is an enlarged view of area JC from FIG. 100F.

FIG. 101 is a perspective view of a first surface of another embodimentof a fluid routing plug.

FIG. 102 is an elevational view of the first surface of the fluidrouting plug shown in FIG. 101 .

FIG. 103 is a cross-sectional view of the fluid routing plug shown inFIG. 102 , taken along line AG-AG.

FIG. 104 is a top plan view of the fluid routing plug shown in FIG. 101.

FIG. 105 is a perspective view of a second surface of the fluid routingplug shown in FIG. 101 .

FIG. 106 is an elevational view of the second surface of the fluidrouting plug shown in FIG. 101 .

FIG. 107 is a cross-sectional view of the fluid routing plug shown inFIG. 106 , taken along line AH-AH.

FIG. 108 is the cross-sectional view of the fluid end section shown inFIG. 50 , but the fluid routing plug from FIG. 101 is shown installedwithin the housing.

FIG. 109 is the cross-sectional view of the fluid end section shown inFIG. 51 , but the fluid routing plug from FIG. 101 is shown installedwithin the housing.

FIG. 110 is a top plan view of another embodiment of a suction anddischarge valve.

FIG. 111 is a perspective view of a second surface of the suction anddischarge valve shown in FIG. 110 .

FIG. 112 is an elevational view of a second surface of the suction anddischarge valve shown in FIG. 110 .

FIG. 113 is a perspective view of a first surface of the suction anddischarge valve shown in FIG. 110 .

FIG. 114 is a cross-sectional view of the suction and discharge valveshown in FIG. 112 , taken along line AI-AI.

FIG. 115 is the cross-sectional view of the fluid end section shown inFIG. 65 , but another embodiment of a fluid routing plug is showninstalled within the housing.

FIG. 116 is an enlarged view of area AJ shown in FIG. 115 .

FIG. 117 is an enlarged view of area AK shown in FIG. 115 .

FIG. 118 is the cross-sectional view of the fluid end section shown inFIG. 65 , but another embodiment of a fluid routing plug is showninstalled within the housing.

FIG. 119 is an enlarged view of area AL shown in FIG. 118 .

FIG. 120 is an enlarged view of area AM shown in FIG. 118 .

FIG. 121 is a top plan view of another embodiment of a fluid routingplug.

FIG. 122 is a perspective view of a second surface of the fluid routingplug shown in FIG. 121 , with a plurality of second fluid passagesformed within the plug shown by phantom lines.

FIG. 123 is an elevational view of the second surface of the fluidrouting plug shown in FIG. 121 , with a plurality of second fluidpassages formed within the plug shown by phantom lines.

FIG. 124 is a cross-sectional view of the fluid routing plug shown inFIG. 123 , taken along line AN-AN.

FIG. 125 is a cross-sectional view of the fluid routing plug shown inFIG. 121 , taken along line AO-AO.

FIG. 126 is the top plan view of the fluid routing plug shown in FIG.121 , with the plurality of second fluid passages formed within the plugshown by phantom lines.

FIG. 127 is an elevational view of a first surface of the fluid routingplug shown in FIG. 121 , with a plurality of second fluid passagesformed within the plug shown by phantom lines.

FIG. 128 is a perspective view of the first surface of the fluid routingplug shown in FIG. 121 .

FIG. 128A is a perspective view of a second surface of anotherembodiment of a fluid routing plug.

FIG. 128B is an elevational view of the second surface of the fluidrouting plug shown in FIG. 128A.

FIG. 128C is a cross-sectional view of the fluid routing plug shown inFIG. 128A, taken along line KA-KA.

FIG. 128D is a top plan view of the fluid routing plug shown in FIG.128A.

FIG. 128E is a perspective view of a first surface of the fluid routingplug shown in FIG. 128A.

FIG. 128F is an elevational view of the first surface of the fluidrouting plug shown in FIG. 128A.

FIG. 128G is a cross-sectional view of the fluid routing plug shown inFIG. 128D, taken along line KB-KB.

FIG. 129 is a top plan view of another embodiment of a fluid routingplug.

FIG. 130 is an elevational view of a second surface of the fluid routingplug shown in FIG. 129 .

FIG. 131 is a cross-sectional view of the fluid routing plug shown inFIG. 130 , taken along line AP-AP.

FIG. 132 is a front right-side perspective view of the high pressurepump shown in FIG. 6 .

FIGS. 133-138 are views of the high pressure pump shown in FIG. 132 withthe drive section and base section removed.

FIG. 139 is a front right-side perspective view of the power end shownin FIG. 132 .

FIG. 140 is an exploded view of the power end shown in FIG. 139 .

FIGS. 141-143 are views of a spacer.

FIGS. 144-149 and 149A are cutaway views of the power end shown in FIG.139 .

FIG. 150 is a front perspective exploded view of the power end shown inFIG. 139 .

FIGS. 151-153 are cutaway views of portions of the power end shown inFIG. 139 .

FIGS. 154-161 are various views of a second nut shown in FIG. 150 .

FIG. 162 is a front perspective view of the front support plates and thecrosshead section shown in FIG. 139 .

FIG. 163 is a rear perspective view of the central support plate andcrosshead section shown in FIG. 139 .

FIG. 164 is a front perspective exploded view of the crosshead frame andcrosshead assembly shown in FIG. 139 .

FIG. 165 is a cutaway sideview of the crosshead section shown in FIG.139 .

FIGS. 166-168 are various views of the pony rod seal housing shown inFIG. 164 .

FIGS. 169-176 are various views of the crosshead frame shown in FIG. 164.

FIGS. 177 and 178 are side views of the crosshead assembly shown in FIG.164 .

FIG. 179 is a front perspective exploded view of the crank section andthe rear support plate shown in FIG. 139 .

FIG. 180 is a rear perspective view of the crank section, the rearsupport plate, and the first set of rods shown in FIG. 139 .

FIG. 181 is a cutaway sideview of the crank section shown in FIG. 139 .

FIGS. 182-186 are various views of the crank frame shown in FIG. 179 .

FIG. 187 is a perspective view of an embodiment of the crankshaft shownin FIG. 179 .

FIG. 188 is a perspective view of another embodiment of a crankshaft.

FIG. 189 is side view of the crankshaft shown in FIG. 187 with dashedlines showing various internal structures.

FIG. 190 is a top perspective and partially exploded view of the basesection used with the high-pressure hydraulic fracturing pump shown inFIG. 132 .

DETAILED DESCRIPTION

Turning now to the non-prior art figures, FIG. 6 shows a high pressurepump 101. The high pressure pump 101 comprises a fluid end 100 attachedto a power end 103. The fluid end 100 may be referred to as a fluid endassembly 100 and the power end 103 may be referred to as a power endassembly 103. In the following description, various embodiments of thefluid end 100 are described in detail with reference to FIGS. 6A-131 .Various embodiments of the power end 103 are described in detail withreference to FIGS. 132-190 .

Fluid End 100

FIGS. 6A and 7 show a fluid end 100. Unlike the traditional fluid end46, shown in FIG. 3 , the fluid end 100 comprises a plurality of fluidend sections 102 rather than a single housing 48. The fluid end sections102 are positioned in a side-by-side relationship. Preferably, the fluidend 100 comprises five fluid end sections 102. However, more or lessfluid end sections 102 may be used. Forming the fluid end 100 out ofmultiple fluid end sections 102 allows a single fluid end section 102 tobe replaced, if needed. In contrast, the entire housing 48 intraditional fluid ends 46 may need to be replaced if only a portion ofthe housing 48 fails.

Turning to FIGS. 8 and 9 , each fluid end section 102 comprises ahorizontally positioned housing 104 having a generally cylindricalcross-sectional shape, as shown in FIG. 8 . In alternative embodiments,each fluid end section may have a generally rectangular cross-sectionalshape. Unlike the traditional fluid end 46 shown in FIGS. 3 and 5 , eachhousing 104 does not include a vertical bore intersecting a horizontalbore to form an internal chamber. Rather, each housing 104 only has asingle horizontally positioned bore 106, as shown in FIG. 9 . Removingthe internal chamber found in traditional fluid ends from the housing104 removes common stress points from the housing 104.

Eliminating the intersecting bore also reduces the cost of manufacturingthe fluid end 100 as compared to traditional fluid ends. The timerequired to manufacture the fluid end 100 is greatly reduced without theneed for machining an intersecting bore, and the fluid end 100 may bemanufactured on a lathe instead of a machining center. The fluid end 100may also be manufactured out of lower strength and less costly materialssince it does not include the high stress areas found in traditionalfluid ends. Each housing 104 may be manufactured out of high strengthalloy steel, such as carbon steel. In alternative embodiments, eachhousing 104 may be manufactured out of stainless steel.

Continuing with FIGS. 8 and 9 , each housing 104 comprises a first outersurface 108 joined to an opposed second outer surface 110 by anintermediate outer surface 112. The horizontal bore 106 extends throughthe housing 104 along a central longitudinal axis 114 and interconnectsthe opposed first and second outer surfaces 108 and 110, as shown inFIG. 9 . Each housing 104 is of single piece construction.

Since each housing 104 only has a single horizontal bore 106, fluid mustbe routed throughout the housing 104 differently from how fluid isrouted throughout a traditional fluid end housing 48. As will bedescribed in more detail herein, a fluid routing plug 116, shown inFIGS. 52-64 , is installed within each housing 104 and is configured toroute fluid throughout the housing 104.

With reference to FIGS. 6A, 7, and 10-16 , each housing 104 is supportedon a single connect plate 118 in a one-to-one relationship. A pluralityof sets of stay rods 120, shown in FIG. 6A, are used to attach eachconnect plate 118 to the power end 103. A spacer 122 is installed oneach stay rod 120 and is configured to engage with a front surface ofthe power end 103, as described later herein.

The connect plates 118 may each be attached to the corresponding stayrods 120 prior to attaching a housing 104 to a corresponding connectplate 118. Because the housings 104 are each attached to a connect plate118, the fluid end 100 does not include a flange like the flange 50formed in the fluid end 46 shown in FIG. 3 . In an alternativeembodiment, multiple housings may be attached to a single, largerconnect plate. In such embodiment, the stay rods are likewise attachedto the single, larger connect plate.

With reference to FIGS. 10-13 , each connect plate 118 has a generallyrectangular shape and has opposed first and second surfaces 124 and 126.A plurality of first passages 128 are formed around the outer peripheryof each connect plate 118. Each first passage 128 interconnects thefirst and second surfaces 124 and 126 of the connect plate 118 and isconfigured for receiving a stay rod 120. Each stay rod 120 extendsthrough a corresponding passage 128 in a one-to-one relationship.

The connect plate 118 shown in FIGS. 10-13 has four first passages 128.Likewise, four stay rods 120 are shown attached to each connect plate118 in FIG. 6A. In alternative embodiments, the connect plate may havemore than four or less than four first passages, as long as the amountof first passages corresponds with the number of stay rods being usedwith each connect plate.

Once each stay rod 120 is installed in a connect plate 118, a first end130 of each stay rod 120 projects from the first surface 124 of theconnect plate 118, as shown in FIG. 16 . A nut 132 and a washer 134 areinstalled on the projecting first end 130 of each stay rod 120 in aone-to-one relationship. The nut 132 is turned until it tightly engagesa corresponding washer 134 and the first surface 124 of the connectplate 118, thereby securing the connect plate 118 to the stay rods 120.

With reference to FIGS. 6, and 14-16 , a plurality of notches 136 areformed around the periphery of the housing 104 at its second surface110, as shown in FIGS. 14 and 15 . When the housing 104 is attached tothe connect plate 118, each notch 136 partially surrounds one of thefirst passages 128 in a one-to-one relationship. The notches 136 providespace to access the washer 134 and nut 132 during operation.

Continuing with FIGS. 10-13 , a central bore 138 is formed in eachconnect plate 118 and interconnects the first and second surfaces 124and 126. The central bore 138 is configured for receiving a stuffing box140, as described in more detail later herein. A plurality of secondpassages 142 are formed in the connect plate 118 and surround thecentral bore 138. Each second passage 142 interconnects the first andsecond surfaces 124 and 126 of the connect plate 118. The secondpassages 142 are configured to align in a one-to-one relationship with aplurality of first threaded openings 144 formed in the second surface110 of each housing 104, as shown in FIGS. 14 and 15 .

Each housing 104 is attached to the first surface 124 of a correspondingconnect plate 118 using a fastening system 146. The fastening system 146comprises a plurality of studs 148, a plurality of washers 150, and aplurality of nuts 152, as shown in FIGS. 7 and 17 . A first end 154 ofeach stud 148 is configured to mate with a corresponding one of thefirst openings 144 formed in the housing 104. The second passages 142formed in the connect plate 118 subsequently receive the plural studs148 projecting from the housing 104.

When the housing 104 and the connect plate 118 are brought together, asecond end 156 of each stud 148 projects from the second surface 126 ofthe connect plate 118. A washer 150 and a nut 152 are subsequentlyinstalled on the second end 156 of each stud 148, in a one-to-onerelationship. The nut 152 is turned until it tightly engages the washer150 and the second surface 126 of the connect plate 118, therebysecuring the housing 104 and the connect plate 118 together.

In FIGS. 10-15 , the housing 104 and connect plate 118 each have eightcorresponding first openings 144 and second passages 142. In alternativeembodiments, more than eight or less than eight corresponding openingsand second passages may be formed in the housing and connect plate. Insuch embodiments, the fastening system may comprise the same number ofstuds, washers, and nuts as there are openings and passages. In furtheralternative embodiments, the fastening system may comprise differenttypes of fasteners, such as socket-headed screws.

Continuing with FIGS. 10-15 , a pair of third passages 158 are formed inthe connect plate 118 on opposite sides of the central bore 138. Thethird passages 158 are alignable with a pair of pin holes 160 formed inthe second surface 110 of the housing 104. Each third passage 158 andeach corresponding pin hole 160 is configured to receive a dowel pin ina one-to-one relationship. The dowel pins are used to help align thehousing 104 on the connect plate 118 during assembly. A threaded hole162 may also be formed in a top surface 164 of each connect plate 118,as shown in FIGS. 10 and 11 . The threaded hole 162 is configured forreceiving a lifting eye (not shown) used to lift and support the connectplate 118 during assembly.

In alternative embodiments, the connect plate may have various shapesand sizes other than those shown in FIGS. 10-13 . For example, theconnect plate may be shaped like the various embodiments disclosed inU.S. Provisional Patent Ser. No. 63/053,797, authored by Thomas et al.and filed on Jul. 20, 2020.

Turning back to FIGS. 6A and 7 , in contrast to the traditional fluidend 46, shown in FIG. 3 , the fluid end 100 is configured to receivefluid from two manifolds, rather than just one. The fluid end 100comprises an upper intake manifold 166 and a lower intake manifold 168.Each manifold 166 and 168 is in fluid communication with each fluid endsection 102. Using two different manifolds 166 and 168 allows differenttypes of fluid to be delivered to each fluid end section 102. Forexample, fluid having a higher level of proppant may be delivered viathe upper intake manifold 166, while fluid having a zero to minimallevel of proppant may be delivered via the lower intake manifold 168.

Continuing with FIGS. 6A and 7 , the upper and lower intake manifolds166 and 168 are joined to the fluid end sections 102 via a plurality ofconduits 159. Each conduit 159 is positioned directly below thecorresponding manifold 166 and 168 and extends along a straight linebetween the fluid end section 102 and the corresponding manifold 166 and168. Thus, each conduit 159 and corresponding manifold 166 and 168 havea “T” shape.

Turning to FIGS. 7A and 7B, an alternative embodiment of an upper andlower intake manifold 161 and 163 is shown. The upper and lower intakemanifolds 161 and 163 are joined to the fluid end sections 102 via aplurality of conduits 165. The conduits 165 have an elbow shape. Theelbow shape of the conduits 165 causes the corresponding manifolds 161and 163 to be spaced farther away from a discharge manifold 167, thanthe manifolds 166 and 168. Providing more space between the intakemanifolds 161 and 163 and the discharge manifold 167 provides more spacefor maintenance to different areas of the fluid end 100, when needed.

Turning back to FIG. 9 , an upper and lower intake bore 170 and 172 areformed within the housing 104. Each bore 170 and 172 interconnects theintermediate outer surface 112 and the horizontal bore 106. The upperand lower intake bores 170 and 172 shown in FIG. 9 are collinear. Inalternative embodiments, the upper and lower intake bores may not becollinear.

With reference to FIGS. 6A-9 , the upper intake bore 170 is in fluidcommunication with the upper intake manifold 166, and the lower intakebore 172 is in fluid communication with the lower intake manifold 168.In operation, fluid may be delivered into the housing 104 through boththe upper and lower intake bores 170 and 172. In alternativeembodiments, only one intake bore may be formed in the housing and onlyone intake manifold may be attached to the housing.

Continuing with FIGS. 6A-9 , the fluid end 100 further comprises aplurality of discharge conduits 174. Each discharge conduit 174 isattached to one of the fluid end sections 102 in a one-to-onerelationship. A discharge manifold 176 interconnects each of thedischarge conduits 174, as shown in FIGS. 6 and 7 . In alternativeembodiments, the discharge conduits and discharge manifold may be formedas a single unit, like the discharge manifold 167, shown in FIGS. 6, 7Aand 7B.

Continuing with FIG. 9 , a discharge bore 178 is formed in the housing104 and interconnects the intermediate surface 112 and the horizontalbore 106. The discharge bore 178 is positioned between the first surface108 of the housing 104 and the intake bores 170 and 172. The dischargebore 178 is in fluid communication with the discharge conduit 174. Inoperation, fluid to be pressurized enters the housing 104 through theupper and lower intake bores 170 and 172. Pressurized fluid exits thehousing 104 through the discharge bore 178.

With reference to FIG. 18 , the discharge bore 178 has an ovalcross-sectional shape, as shown by a discharge bore opening 180. Theopening 180 has a length A and a width B. The discharge bore 178 isformed within the housing 104 such that the width B extends along anaxis that is parallel to the longitudinal axis 114 of the housing 104.During operation, high fluid pressure within the discharge bore 178 maycause the walls along the length A to compress, causing the dischargebore 178 to have a more circular cross-sectional shape. Providing roomfor the walls surrounding the discharge bore 178 to compress, helpsreduce stress in the housing 104 and increase fluid flow. In alternativeembodiments, the discharge bore may have a circular cross-sectionalshape.

Continuing with FIG. 19 , a counterbore 173 is formed within the housing104 immediately above the opening 180 of the discharge bore 178. Thedischarge bore 178 opens into the counterbore 173. The counterbore 173has a circular cross-sectional shape, as shown by the opening 175 inFIG. 18 . A portion of the discharge conduit 174 is installed within thecounterbore 173 through its opening 175. A seal 182 is interposedbetween the walls of the housing 104 surrounding the discharge bore 178and an outer surface of the discharge conduit 174. The seal 182 isinstalled within a groove 184 formed in the walls of the housing 104.The seal 182 may be identical to the second seal 376, described withreference to FIGS. 65 and 70 . In alternative embodiments, the seal maybe identical to the first seal 374, described with reference to FIGS. 65and 71 .

The groove 184 is characterized by two sidewalls 185 joined to a base183. The sidewalls 185 may join the base 183 via radius corners or at a90 degree angle. No grooves are formed in the outer surface of thedischarge conduit 174 for housing a seal. In operation, the seal 182wears against the outer surface of the discharge conduit 174. If theouter surface of the discharge conduit 174 begins to erode, allowingfluid to leak around the seal 182, the discharge conduit 174 may bereplaced with a new discharge conduit 174.

The discharge bore 178 shown in FIG. 9 interconnects a top surface 113of the intermediate surface 112 of the housing 104 and the horizontalbore 106. Likewise, the discharge conduits 174 shown in FIGS. 6, 7, and9 are attached to the top surface 113 of the intermediate surface 112 ofeach housing 104. In operation, any gas trapped within the housing 104rises towards the top of the housing 104. Placing the discharge bore 178and conduit 174 at the top of the housing 104 allows the gases tonaturally escape. Additionally, any wear caused to the components by therising gas will primarily be imposed on the discharge conduit 174,rather than the housing 104. The discharge conduit 174 and correspondingdischarge piping 176 are easily replaced, if needed.

In alternative embodiments, the discharge bore may interconnect a bottomor side surface of the intermediate surface and the horizontal bore, andthe discharge conduit may be attached to the corresponding surface ofthe housing. In further alternative embodiments, the discharge bore mayinterconnect the first outer surface of the housing and the horizontalbore, and the discharge conduit may be attached to the first outersurface of the housing.

With reference to FIGS. 6, 18 and 19 , a rectangular flange 171 isformed around each discharge conduit 174. Each rectangular flange 171 isattached to the housing 104 using a plurality of threaded studs 186 andnuts 187, as shown in FIGS. 6 and 19 . A plurality of threaded openings188 are formed in the housing 104 for receiving the studs 186, as shownin FIG. 18 . The openings 188 are positioned in a rectangular patternaround the discharge bore opening 180. Such pattern helps maximize thesurface area of the intermediate surface 112 of the housing 104, helpingto reduce the size and weight of the housing 104.

With reference to FIGS. 7 and 18 , the intake manifolds 166 and 168 eachcomprise a plurality of rectangular flanges 189 joined to a plurality ofconduits 191 in a one-to-one relationship, as shown in FIG. 7 . Eachrectangular flange 189 is attached to the housing 104 using a pluralityof threaded studs 190 and nuts 193, as shown in FIG. 7 . A plurality ofthreaded openings 192 are formed in the housing 104 for receiving thestuds 190, as shown in FIG. 18 . The openings 192 are positioned in arectangular pattern around the intake bores 170 and 172 to maximizesurface area of the housing 104. In alternative embodiments, thedischarge conduits and intake manifolds may be attached to the housingusing different types of fasteners, such as socket-headed screws.

Continuing with FIG. 18 , the intermediate surface 112 of the housing104 includes a first portion 194 joined to a second portion 196 by afirst tapered portion 198. The second portion 196 is joined to a thirdportion 200 by a second tapered portion 202. The first portion 194 isjoined to the first surface 108 and the third portion 200 is joined tothe second surface 110.

The second portion 196 has a smaller diameter than both the first andthird portions 194 and 200. Providing the second portion 196 with asmaller diameter helps remove unnecessary weight from the housing 104.The third portion 200 may have a slightly larger diameter than the firstportion 194. The first, second, and third portions 194, 196, and 200 aregenerally cylindrical. Thus, the housing 104 may be characterized asbeing primarily cylindrical. In alternative embodiments, the housing maybe uniform in diameter throughout its intermediate surface. In furtheralternative embodiments, the housing may have various diametersthroughout its intermediate surface other than those shown in FIG. 18 .

Continuing with FIG. 18 , a threaded hole 204 is formed in the topsurface 113 of the intermediate surface 112. The threaded hole 204 ispositioned at the center of gravity of the housing 104 when the housing104 is fully loaded with the components described herein. The threadedhole 204 is configured to receive a lifting eye (not shown) used to liftand support the housing 104 during assembly and maintenance, as shown inFIG. 9 .

With reference to FIGS. 20-29 , each fluid end section 102 furthercomprises a stuffing box 140 attached to the second outer surface 110 ofthe housing 104. The stuffing box 140 has a generally cylindrical shapeand comprises a first outer surface 206 joined to an opposed secondouter surface 208 by an intermediate outer surface 210. The intermediatesurface 210 includes a cylindrical first portion 212 joined directly toa cylindrical second portion 214. The first portion 212 is positionedadjacent the first surface 206 and has a reduced diameter from that ofthe second portion 214. A threaded hole 215 is formed in a top surfaceof the second portion 214. The threaded hole 215 is configured toreceive a lifting eye (not shown) used to lift and support the stuffingbox 140 during assembly and maintenance.

A central passage 216 interconnects the stuffing box's first and secondouter surfaces 206 and 208. The walls surrounding the central passage216 include a first section 218 joined to a second section 220 by atapered shoulder 222, as shown in FIGS. 25, 26, and 29 . The secondsection 220 has a larger diameter than that of the first section 218. Asdescribed in more detail herein, the second section 220 and the taperedshoulder 222 are configured for receiving a plunger packing 224, asshown in FIGS. 20 and 21 .

Continuing with FIGS. 23-29 , a plurality of passages 226 are formedaround the periphery of the second portion 214 of the stuffing box 140.Each passage 226 interconnects the second surface 208 of the stuffingbox 140 and a base 228 of the second portion 214. The passages 226 areformed parallel to the central passage 216.

Turning back to FIGS. 14 and 15 , a plurality of second threadedopenings 230 are formed in the second surface 110 of the housing 104.The openings 230 surround the opening of the horizontal bore 106. Thesecond openings 230 are surrounded by the first openings 144 used withthe connect plate 118.

Continuing with FIGS. 20 and 21 , the walls surrounding the horizontalbore 106 adjacent the second surface 110 of the housing 104 are sized toreceive the first portion 212 of the stuffing box 140. The first portion212 is installed within the horizontal bore 106 such that the base 228of the second portion 214 abuts the second surface 110 of the housing104. A portion of the second portion 214 is disposed within the centralbore 138 formed in the connect plate 118. The stuffing box 140 isaligned on the housing 104 such that the passages 226 align with thesecond openings 230 in a one-to-one relationship.

With reference to FIGS. 20, 21, and 30-37 , the stuffing box 140 isattached to the housing 104 using a retainer 232 and a fastening system234. The retainer 232 has a generally cylindrical shape and comprisesopposed first and second outer surfaces 236 and 238 joined by anintermediate surface 240. A central passage 242 interconnects the firstand second outer surfaces 236 and 238. At least a portion of the centralpassage 242 has internal threads 244. A plurality of side passages 246are formed in the retainer 232. Each passage 246 interconnects thecentral passage 242 and the intermediate surface 240. The passages 246provide a pathway for lubricating oil to be introduced to the horizontalbore 106 during operation. The oil lubricates the moving parts withinthe housing 104 during operation.

Continuing with FIGS. 30-37 , a plurality of passages 248 are formed inthe retainer 232 and surround the central passage 242. Each passage 248interconnects the first and second outer surfaces 236 and 238. The firstsurface 236 of the retainer 232 is positioned on the second surface 208of the stuffing box 140 such that the passages 248 align with thepassages 226 formed in the stuffing box 140, in a one-to-onerelationship.

A pair of dowel pin holes 241 are formed in the second surface 208 ofthe stuffing box 140, as shown in FIGS. 27 and 28 . A corresponding pairof dowel pin holes 243 are formed in the first surface 236 of theretainer 232, as shown in FIGS. 31 and 32 . The holes 241 and 243 areconfigured for receiving a dowel pin. The dowel pin aligns the retainer232 on the stuffing box 140 during assembly.

Turning back to FIGS. 20 and 21 , the fastening system 234 secures boththe retainer 232 and the stuffing box 140 to the housing 104. Thefastening system 234 comprises a plurality of studs 250, nuts 252, andwashers 254. A first end 256 of each stud 250 mates with one of thesecond openings 230 in the housing 104 in a one-to-one relationship. Thepassages 226 in the stuffing box 140 and the passages 248 in theretainer 232 subsequently receive the plural studs 250 projecting fromthe housing 104.

A second end 258 of each stud 250 projects from the second surface 238of the retainer 232. The projecting second end 258 of each stud 250receives a washer 254 and a nut 252. The nut 252 is turned until ittightly engages the washer 254 and the second surface 238 of theretainer 232, thereby securing the retainer 232 and the stuffing box 140together. The retainer 232, in turn, holds the stuffing box 140 againstthe housing 104. The stuffing box 140 and the retainer 232 may beattached to and removed from the housing 104 without removing theconnect plate 118.

When the first portion 212 of the stuffing box 140 is installed withinthe housing 104, a seal 260 is interposed between the walls of thehousing 104 and outer surface of the first portion 212. The seal 260 isinstalled within a groove 262 formed in the walls of the housing 104.The seal 260 may be identical to the first seal 374, described withreference to FIGS. 65 and 71 . In alternative embodiments, the seal maybe identical to the second seal 376, described with reference to FIGS.65 and 70 .

The groove 262 is characterized by two sidewalls 264 joined by a base266, as shown in FIG. 21 . The sidewalls 264 may join the base 266 viaradius corners or at a 90 degree angle. No grooves are formed in thefirst portion 212 of the stuffing box 140 for housing a seal. The seal260 wears against the outer surface of the first portion 212 duringoperation. If the outer surface of the first portion 212 begins toerode, allowing fluid to leak around the seal 260, the stuffing box 140may be replaced with a new stuffing box 140.

When the stuffing box 140 is attached to the housing 104 using thefastening system 234, a first end 256 of the studs 250 may be installedwithin the housing 104 such that they extend past the seal 260, as shownin FIG. 20 . An edge of the studs 250 may not be purposely aligned withan edge of the seal 260 in order to prevent areas of high stress frombeing aligned with one another in the housing 104, potentially causing astress riser.

Continuing with FIGS. 20, 21, and 38-42 , a plunger packing 224 isinstalled within the central passage 216 of the stuffing box 140. Theplunger packing 224 engages the tapered shoulder 222 and is positionedwithin the second section 220 of the central passage 216, as shown inFIGS. 20 and 21 . A portion of the plunger packing 224 may extend intothe central passage 242 of the retainer 232. The plunger packing 224 hasa central passage 268 that aligns with the central passages 216 and 242when the plunger packing 224 is installed within the stuffing box 140and the retainer 232. In alternative embodiments, the plunger packingmay be sized to not extend into the retainer.

The plunger packing 224 comprises a pair of outer ring seals 270 and 271and at least one inner ring seal 272. The outer ring seals 270 and 271may be made of metal while the inner ring seals 272 may be made of anelastomer material. The outer ring 270 has a tapered outer surface 274that is sized to engage the tapered shoulder 222 formed in the centralpassage 216. The tapered engagement helps reduce stress in the stuffingbox 140 during operation. In alternative embodiments, the wallssurrounding the central passage of the stuffing box may include anannular shoulder rather than a tapered shoulder. In such embodiment, theplunger packing may have a flat outer ring configured to mate with theannular shoulder. A plurality of holes 275 are formed in the outer ring271. The holes 275 are in fluid communication with the side passages 246formed in the retainer 232 in order to deliver lubricating oil to thehousing 104.

With reference to FIGS. 20, 21, and 43-46 , a packing nut 276 isinstalled within the retainer 232 and engages the plunger packing 224.The packing nut 276 comprises a first surface 278 joined to an opposedsecond surface 280 by an intermediate surface 282. A central passage 284extends through the packing nut 276 and interconnects the opposed firstand second surfaces 278 and 280. A plurality of side holes 286 areformed in the packing nut 276 and interconnect the central passage 284and the intermediate surface 282. The holes 286 are configured forengaging a tool used to grip the packing nut 276.

Continuing with FIGS. 43-46 , external threads 288 are formed in aportion of the intermediate surface 282 of the packing nut 276. Theexternal threads 288 are configured to mate with the internal threads244 formed within the retainer 232, as shown in FIGS. 20 and 21 . Themating threads 288 and 244 are buttress threads. The buttress threadsare configured to handle a large amount of load using a low amount ofthreads. Using a low amount of threads allows the packing nut 276 to bequickly removed or installed within the retainer 232. In alternativeembodiments, the packing nut and retainer may mate using traditionalthreads.

When the packing nut 276 is installed within the retainers 232, thefirst surface 278 of the packing nut 276 engages an outer ring seal 270of the plunger packing 224. Such engagement compresses the plungerpacking 224, creating a tight seal. After the packing nut 276 has beeninstalled within a retainer 232, the central passage 284 within thepacking nut 276 is aligned with the central passage 268 in the plungerpacking 224.

Continuing with FIGS. 20 and 21 , when the stuffing box 140 and theretainer 232 are attached to the housing 104, the central passages 216and 242 align with the horizontal bore 106. Likewise, the centralpassages 268 and 284 in the installed plunger packing 224 and packingnut 276 align with the horizontal bore 106. Thus, the central passages216, 242, 268, and 284 may be considered an extension of the horizontalbore 106. A plunger 290 is disposed with the installed plunger packing224 and the packing nut 276, as shown in FIG. 20 . In operation, theplunger 290 reciprocates within the horizontal bore 106 in order topressurize fluid contained with the housing 104.

With reference to FIGS. 20, 21, and 47-49 , the horizontal bore 106 issealed at the first surface 108 of the housing 104 by a retainer 300.The retainer 300 has a first surface 302 joined to an opposed secondsurface 304 by an outer intermediate surface 306. A cutout 308 is formedin the second surface 304 for receiving a portion of a discharge valveguide 298. A central passage 310 is formed in the retainer 300 andinterconnects the first surface 302 and the cutout 308. The wallssurrounding the central passage 310 have a polygonal shape. Thepolygonal shape is configured to mate with a tool used to grip theretainer 300.

The intermediate surface 306 of the retainer 300 has external threads312 that mate within internal threads 314 formed in the wallssurrounding the horizontal bore 106 adjacent the first surface 108 ofthe housing 104, as shown in FIGS. 20 and 21 . The mating threads 312and 314 are buttress threads. The buttress threads are configured tohandle a large amount of load using a low amount of threads. Using a lowamount of threads allows the retainer 300 to be quickly removed from orinstalled within the housing 104. In alternative embodiments, theretainer may mate with the housing using traditional threads. In furtheralternative embodiments, the retainer may be secured to the housingusing a fastening system, like the fastening system 234.

Turning now to FIGS. 50 and 51 , the fluid routing plug 116 is installedwithin a medial section of the horizontal bore 106. The fluid routingplug 116 is configured to engage with a suction valve 292 on one sideand a discharge valve 294 on the opposite side. In operation, thesuction and discharge valves 292 and 294 move axially along an axis thatis parallel to or aligned within the central longitudinal axis 114 ofthe housing 104, shown in FIG. 9 , as the valves 292 and 294 move atalternating times between an open and closed position. In the closedposition, the valves 292 and 294 are pressed against the fluid routingplug 116, preventing fluid from exiting the plug 116. In the openposition, the valves 292 and 294 are spaced from the fluid routing plug116, allowing fluid to flow from the plug 116.

As will be described in more detail herein, axial movement of thesuction valve 292 is limited by a suction valve guide 296 installedwithin the housing 104. Likewise, axial movement of the discharge valve294 is limited by the discharge valve guide 298 installed within thehousing 104.

Turning now to FIGS. 52-64 , the fluid routing plug 116 comprises a body316 having opposed first and second outer surfaces 318 and 320 joined byan intermediate outer surface 322. The first outer surface 318 may alsobe referred to as the suction side of the fluid routing plug 116. Thesecond outer surface 320 may also be referred to as the discharge sideof the fluid routing plug 116. A central longitudinal axis 324 extendsthrough the body 316 and both surfaces 318 and 320, as shown in FIG. 55.

A plurality of first fluid passages 326 are formed within the body 316and interconnect the intermediate surface 322 and the first surface 318.The first fluid passages 326 interconnect the intermediate surface 322and the first surface 318 by way of an axial-blind bore 328, as shown inFIG. 55 . The blind bore 328 extends along the central longitudinal axis324 of the body 316. The first fluid passages 326 each open into theblind bore 328 via a plurality of openings 330. A longitudinal axis 332of each first fluid passage 326 intersects the central longitudinal axis324 of the body 316, as shown in FIG. 58 .

The fluid routing plug 116 shown in FIGS. 52-64 has four first fluidpassages 326 formed in its body 316. The first fluid passages 326 areequally spaced around the body 316. In alternative embodiments, morethan four or less than four first fluid passages may be formed in thebody and may be equally or unequally spaced apart from one another.

Continuing with FIG. 55 , the first fluid passages 326 extend betweenthe intermediate surface 322 and the blind bore 328 at a non-right anglerelative to the central longitudinal axis 324—the acute angle facing thesecond surface 320 of the body 316. Forming the first fluid passages 326at such an angle reduces the amount of stress in the fluid routing plug116 as fluid flows through the first fluid passages 326. Forming thefirst fluid passages 326 at such angle also helps direct fluid flowtowards the blind bore 328 and the first surface 318.

With reference to FIGS. 57 and 59 , the first fluid passages 326 have anoval cross-sectional shape, as shown by an opening 334 of each firstfluid passage 326 on the intermediate surface 322. Each opening 334 hasa length A and a width B, as shown in FIG. 59 . The first fluid passages326 are formed in the body 316 such that the length A extends along anaxis that is parallel to the central longitudinal axis 324 of the body316. Orienting the first fluid passages 326 as such helps reduce theamount of stress in the body 316 as fluid flows through the first fluidpassages 326 and helps maximize the rate of fluid flow through thepassages 326. In alternative embodiments, the first fluid passages mayhave a different cross-sectional shape, such as a circular or oblongshape. In further alternative embodiments, the first fluid passages maybe shaped like the first fluid passages 910, shown in FIGS. 121 and 124.

With reference to FIGS. 60-63 , the fluid routing plug 116 furthercomprises a plurality of second fluid passages 336 formed in the body316. The second fluid passages 336 each have a circular cross-sectionalshape and interconnect the first and second surfaces 318 and 320 of thebody 316. In alternative embodiments, the second fluid passages may havea different cross-sectional shape, such as an oval or oblong shape.

Unlike the first fluid passages 326, the second fluid passages 336 donot intersect an axially blind bore. Rather, each second fluid passage336 extends between the first and second surface 318 and 320 along astraight-line path. The second fluid passages 336 and the first fluidpassages 326 do not intersect and are positioned offset from oneanother, as shown in FIG. 58 . Positioning the first and second passages326 and 336 offset from one another helps minimize the stress in thefluid routing plug 116 during operation. The fluid routing plug 116shown in FIGS. 52-64 has twelve second fluid passages 336 formed in itsbody 316. In alternative embodiments, more or less than twelve secondfluid passages may be formed in the body.

Each second fluid passage 336 extends between the first and secondsurfaces 318 and 320 along a different axis, as shown in FIGS. 60-63 .Each axis is positioned at a non-zero angle relative to the centrallongitudinal axis 324 of the body 316. Forming each second passage 336along a different axis helps alleviate stress in the fluid routing plug116 during operation and helps maximize the rate of fluid flow throughthe second passages 336.

Turning back to FIGS. 53, 55, and 56 , the first surface 318 of the body316 includes an outer rim 338 joined to a tapered wall 340. The outerrim 338 may taper slightly between the intermediate surface 322 and thetapered wall 340, as shown in FIG. 55 . Such taper provides more surfacearea for the tapered wall 340 without increasing the length of theintermediate surface 322. The tapered wall 340 extends between anentrance 342 of the blind bore 328 and the outer rim 338 at an angle ofat least 30 degrees relative to the central longitudinal axis 324 of thebody 316. Preferably, the tapered wall 340 is formed at an angle of 45degrees relative to the central longitudinal axis 324 of the body 316,as is shown in FIG. 55 . As will be described in more detail laterherein, the tapered wall 340 forms a cavity 344 within the first surface318 of the body 316 that is sized to receive a sealing element 346 ofthe suction valve 292, as shown in FIGS. 72-76 .

Continuing with FIGS. 53 and 56 , the second fluid passages 336 open onthe outer rim 338 of the first surface 318, as shown by the openings348. The second fluid passages 336 are formed within the body 316 suchthat the openings 348 are positioned in groups 350 around the outer rim338. The first surface 318 shown in FIG. 59 comprises four groups 350 ofopenings 348, each group 350 comprising three openings 348. Adjacentopenings 348 within each group 350 are equally spaced. The spacingbetween the nearest openings 348 of adjacent groups 350 exceeds thespacing between adjacent openings 348 within a single group 350. Spacingthe openings 348 in groups 350 helps achieve the ideal velocity of fluidflow through the fluid routing plug 116 and allows the second fluidpassages 336 to be offset from the first fluid passages 326, as shown inFIG. 58 . In alternative embodiments, the openings may be spaced indifferently sized groups or different patterns than that shown in FIG.56 .

With reference to FIGS. 52, 54, and 55 , the second surface 320 of thebody 316 comprises an outer rim 352 joined to a central base 354 by atapered wall 356. The tapered wall 356 extends between the central base354 and the outer rim 352 at an angle of at least 30 degrees relative tothe central longitudinal axis 324 of the body 316. Preferably, thetapered wall 356 is formed at an angle of 45 degrees relative to thecentral longitudinal axis 324 of the body 316, as is shown in FIG. 55 .As will be described in more detail later herein, the tapered wall 356forms a cavity 358 within the second surface 320 of the body 316 that issized to receive a sealing element 360 of the discharge valve 294, asshown in FIGS. 85-89 .

Continuing with FIGS. 52, 54, and 55 , a blind bore 362 is formed in thecenter of the central base 354. The walls surrounding the blind bore 362may be configured to mate with a tool used to grip the fluid routingplug 116. For example, the walls surrounding the blind bore 362 may bethreaded. The second fluid passages 336 open on the central base 354 ofthe second surface 320, as shown by the openings 364 in FIGS. 52 and 54. The second fluid passages 336 are formed within the body 316 such thatthe openings 364 surround the opening of the blind bore 362. Theopenings 364 shown in FIG. 54 are all equally spaced from one anotheraround the opening of the blind bore 362. In alternative embodiments,the openings of the second fluid passages on the central base may notall be equally spaced apart from one another.

Continuing with FIG. 55 , in order to provide space for the openings 364on the second surface 320, the tapered wall 356 has a greater diameterthan the tapered wall 340 formed in the first surface 318. Thus, as willbe described in more detail herein, the sealing element 360 of thedischarge valve 294 is larger in size than the sealing element 346 ofthe suction valve 292, as shown in FIGS. 72-76 and 85-89 .

Turning back to FIGS. 50 and 51 , the fluid routing plug 116 isinstalled within the horizontal bore 106 such that the first fluidpassages 326 are in fluid communication with the upper and lower intakebores 170 and 172. The upper and lower intake bores 170 and 172 directfluid into the first fluid passages 326 of the fluid routing plug 116.The first fluid passages 326 direct the fluid into the blind bore 328and towards the first surface 318 of the fluid routing plug 116.

When the plunger 290 is retracted from the housing 104, the fluidflowing through the first fluid passages 326 forces the suction valve292 to move axially away from the first surface 318. Such position isconsidered an open position of the suction valve 292. When the suctionvalve 292 is spaced from the first surface 318, fluid flows out of theblind bore 328, through the gap between the first surface 318 and thesuction valve 292. From there, the fluid flows around the suction valve292 and the suction valve guide 296 and into the horizontal bore 106. Afirst fluid flow path for the fluid to be pressurized is shown by thearrows 366 in FIG. 50 .

With reference to FIG. 51 , as the plunger 290 extends into thehorizontal bore 106, the plunger 290 forces fluid in the horizontal bore106 back towards the fluid routing plug 116. Pressurized fluid forcedback towards the fluid routing plug 116 by the plunger 290 forces thesuction valve 292 to seal against the first surface 318, sealing theentrance 342 of the blind bore 328. Such position is considered a closedposition of the suction valve 292. Once the entrance 342 of the blindbore 328 is sealed, the only place for fluid to flow is through theopenings 348 of the second fluid passages 336 on the outer rim 338 ofthe first surface 318.

Fluid flows into the openings 348 on the first surface 318 and throughthe second passages 336 towards the second surface 320 of the fluidrouting plug 116. The pressurized fluid at the second surface 320 forcesthe discharge valve 294 to move axially away from the second surface320, unsealing the openings 364 of the second fluid passages 336. Suchposition is considered an open position of the discharge valve 294.Pressurized fluid is then allowed to flow around the discharge valve 294and into the discharge bore 178. A second fluid flow path for thepressurized fluid is shown by the arrows 368 in FIG. 51 .

When the plunger 290 retracts from the housing 104, the fluid pressureon the back side of the discharge valve 294 is greater than the fluidpressure within the fluid routing plug 116. Such pressure differentialcauses the discharge valve 294 to seal against the second surface 320,sealing the openings 364 of the second fluid passages 336. Such positionis considered the closed position of the discharge valve 294.

Turning to FIG. 64 , the intermediate surface 322 of the fluid routingplug 116 varies in diameter throughout its length and generallydecreases in size from its second surface 320 to its first surface 318.The intermediate surface 322 comprises a first sealing surface 370positioned adjacent the first surface 318 and a second sealing surface372 positioned adjacent the second surface 320. The first and secondsealing surfaces 370 and 372 each extend around the entire intermediatesurface 322 in an endless manner and surround the longitudinal axis 324of the body 316. The first and second sealing surfaces 370 and 372 shownin FIG. 64 are annular. In alternative embodiments, the first and secondsealing surfaces may have non-annular shape, such as an oval shape.

The first sealing surface 370 has a smaller diameter than the secondsealing surface 372. As will be described in more detail herein, thefirst and second sealing surfaces 370 and 372 are configured to engage afirst and second seal 374 and 376 installed within the housing 104, asshown in FIGS. 70 and 71 .

Continuing with FIG. 64 , the intermediate surface 322 of the fluidrouting plug 116 further comprises a first bevel 378 positioned betweenthe opening 334 of the first fluid passages 326 and the first sealingsurface 370. The first bevel 378 extends around the entire intermediatesurface 322 in an endless manner and surrounds the longitudinal axis 324of the body 316. The first bevel 378 shown in FIG. 64 is annular. Inalternative embodiments, the first bevel may have non-annular shape,such as an oval shape.

A maximum diameter of the first bevel 378 is greater than the diameterof the first sealing surface 370. The maximum diameter of the firstbevel 378 is positioned adjacent the openings 334 of the first fluidpassages 326 and a minimum diameter of the first bevel 378 is positionedadjacent the first sealing surface 370. As will be described in moredetail later herein, the first bevel 378 corresponds with a firstbeveled surface 380 formed in the housing 104, as shown in FIGS. 65 and69 .

The intermediate surface 322 also comprises a second bevel 382positioned between the second sealing surface 372 and the openings 334of the first fluid passages 326. The second bevel 382 extends around theentire intermediate surface 322 in an endless manner and surrounds thelongitudinal axis 324 of the body 316. The second bevel 382 shown inFIG. 64 is annular. In alternative embodiments, the second bevel mayhave a non-annular shape, such as an oval shape.

A maximum diameter of the second bevel 382 is positioned adjacent thesecond sealing surface 372 and a minimum diameter of the second bevel382 is positioned adjacent the openings 334 of the first fluid passages326. The second sealing surface 372 and the maximum diameter of thesecond bevel 382 both have a greater diameter than the maximum diameterof the first bevel 378 and the diameter of the first sealing surface370.

As will be described in more detail later herein, the second bevel 382corresponds with a second beveled surface 384 formed in the housing 104,as shown in FIGS. 65 and 68 . A small transition bevel 386 may extendbetween the second sealing surface 372 and the second bevel 382.However, the transition bevel 386 does not engage the second beveledsurface 384, as shown in FIG. 68 . The transition bevel 386 helps reducefriction between the fluid routing plug 116 and the housing 104 duringinstallation.

As described above, the first and second bevels 378 and 382 arepositioned between the first and second sealing surfaces 370 and 372.The first and second bevels 378 and 382 help alleviate stress in thefluid routing plug 116 during operation. In alternative embodiments, theintermediate surface may only include a single bevel positioned betweenthe first and second sealing surfaces.

Continuing with FIG. 64 , the various diameters of the intermediatesurface 322 are shown in more detail. The first sealing surface 370 hasa diameter D1. The maximum diameter of the first bevel 378 has adiameter D2. The maximum diameter of the second bevel 382 has a diameterD3, and the second sealing surface 372 has a diameter D4. As describedabove in detail, D4 is greater than D3, D3 is greater than D2, and D2 isgreater than D1.

With reference to FIG. 65 , in addition to being shaped to alleviatestress, the intermediate surface 322 is shaped to allow for easyinstallation of the fluid routing plug 116 within the horizontal bore106. The fluid routing plug 116 is installed into the horizontal bore106 at the first outer surface 108 of the housing 104. The fluid routingplug 116 is installed with the first surface 318 entering the horizontalbore 106 before the second surface 320. The fluid routing plug 116 ispushed into the horizontal bore 106 until the first sealing surface 370engages the first seal 374 and the second sealing surface 372 engagesthe second seal 376.

The first sealing surface 370 and first bevel 378 have smaller diametersthan the second seal 376 and the second beveled surface 384. Thus,clearance exists between these features as the fluid routing plug 116 isinstalled into the horizontal bore 106. Providing such clearance duringinstallation avoids unnecessary wear to both the housing 104 and fluidrouting plug 116 during installation.

With reference to FIGS. 65 and 67 , once the fluid routing plug 116 isinstalled within the housing 104, an annular chamber 388 is formedbetween the walls of the housing 104 and the intermediate surface 322.The intake bores 170 and 172 open into the chamber 388. Only a couple ofthe openings 334 of the first fluid passages 326 may align with theintake bores 170 and 172. Alternatively, the fluid routing plug 116 maybe installed within the housing 104 such that none of the openings 334directly align with the intake bores 170 and 172. The chamber 388provides a pathway for fluid from the intake bores 170 and 172 to flowaround the fluid routing plug 116 and into the openings 334 of the firstfluid passages 326. The chamber 388 also provides space for proppant orother debris to collect during operation.

Continuing with FIG. 67 , the walls of the housing 104 surrounding thehorizontal bore 106 immediately adjacent the intake bores 170 and 172are beveled, as shown by bevels 390 and 392. The bevels 390 and 392 helpreduce stress in the housing 104 during operation and increase the sizeof the annular chamber 388. In alternative embodiments, the bevels 390and 392 may be larger than those shown in FIG. 67 in order to increasethe size of the chamber 388, as shown for example in FIG. 100F.Similarly, the walls of the housing 104 surrounding the horizontal bore106 immediately adjacent the discharge bore 178 are also beveled, asshown by the bevel 394 in FIG. 66 . The bevel 394 reduces stress in thehousing 104 during operation and helps direct fluid into the dischargebore 178.

Continuing with FIGS. 65 and 68 , the second bevel 382 and the secondbeveled surface 384 are shown in more detail. The second beveled surface384 is positioned between the second seal 376 and the intake bores 170and 172. The second beveled surface 384 has an annular shape andsurrounds the horizontal bore 106 in an endless manner. In alternativeembodiments, the second beveled surface may have a shape that conformsto the shape of the second bevel formed in the fluid routing plug.

When the fluid routing plug 116 is installed within the horizontal bore106, the second bevel 382 seats against the second beveled surface 384,as shown in FIG. 68 . The bevels 382 and 384 meet at a non-right angle.Such angle reduces stress in the fluid routing plug 116 and the housing104 during operation. The bevels 382 and 384 remain engaged during theforward and backwards stroke of the plunger 290.

Turning to FIGS. 65 and 69 , the first bevel 378 and the first beveledsurface 380 are shown in more detail. The first beveled surface 380 ispositioned between the intake bores 170 and 172 and the first seal 374.The first beveled surface 380 has an annular shape and surrounds thehorizontal bore 106 in an endless manner. In alternative embodiments,the first beveled surface may have a shape that conforms to the shape ofthe first bevel formed in the fluid routing plug.

In contrast to the second bevel 382, the first bevel 378 is sized to bespaced from the first beveled surface 380 when the fluid routing plug116 is initially installed within the housing 104, as shown by a gap398. The gap 398 provides space for the fluid routing plug 116 to expandduring operation.

As the plunger 290 retracts backwards away from the housing 104, asignificant amount of load is applied to the second bevel 382. Theapplied load causes the fluid routing plug 116 to slightly compress,forcing the intermediate surface 322 at the first bevel 378 to expandoutwards. As the first bevel 378 expands, it eventually engages with thefirst beveled surface 380. Upon engaging the first beveled surface 380,the load being applied to the second bevel 382 is shared with the firstbevel 378, thereby decreasing the load applied to the second bevel 382.Without the gap 398, the fluid routing plug 116 would not have room toexpand, potentially causing damage to the fluid routing plug 116 and thehousing 104 over time.

As the plunger 290 extends forward into the housing 104, the first bevel378 will return to its un-expanded state, re-creating the gap 398. Thegap 398 will repeatedly be created and closed during operation as theplunger 290 reciprocates. In addition to providing space for the fluidrouting plug 116 to expand, the gap 398 also provides a gas and fluidrelief area during the forward stroke of the plunger 290.

Continuing with FIGS. 68 and 69 , because the second bevel 382 carriesthe majority of the load experienced by the fluid routing plug 116during operation, the second bevel 382 is longer than the first bevel378. In alternative embodiments, the first bevel may be longer than thatshown in FIG. 69 or be equal in length to the second bevel. In suchembodiments, the first beveled surface formed in the housing maycorrespond with the chosen size of the first bevel. In furtheralternative embodiments, the first bevel may be sized to mate with thefirst beveled surface when the fluid routing plug is first installedwithin the housing.

With reference to FIGS. 65, 70, and 71 , in order to prevent fluid fromleaking around the fluid routing plug 116 during operation, the firstand second seals 374 and 376 are positioned between the sealing surfaces370 and 372 and the walls of the housing 104 surrounding the horizontalbore 106.

The first seal 374 is positioned within a first annular groove 400formed in housing 104 and surrounding the horizontal bore 106 in anendless manner. The first groove 400 is positioned between the intakebores 170 and 172 and the second outer surface 110 of the housing 104,as shown in FIG. 65 . The first groove 400 is characterized by twosidewalls 402 joined by a base 404, as shown in FIG. 71 . The sidewalls402 may join the base 404 via radius corners or at a 90 degree angle. Inalternative embodiments, the first groove may have a non-concentricshape that corresponds with the shape of the first sealing surface.

The second seal 376 is positioned within a second annular groove 406formed in the housing 104 and surrounding the horizontal bore 106 in anendless manner. The second groove 406 is positioned between thedischarge bore 178 and the intake bores 170 and 172, as shown in FIG. 65. The second groove 406 is characterized by two sidewalls 408 joined bya base 410. The sidewalls 408 may join the base 410 via radius cornersor at a 90 degree angle. In alternative embodiments, the second groovemay have a non-concentric shape that corresponds with the shape of thesecond sealing surface.

The second groove 406 has a larger diameter than that of the firstgroove 400 due to the diameter of the horizontal bore 106 at eachgroove, as shown in FIG. 65 . Likewise, the second seal 376 has a largerdiameter than that of the first seal 374. Because the first and secondgrooves 400 and 406 are formed in the housing 104, no grooves are formedin the intermediate surface 322 of the fluid routing plug 116 forreceiving a seal.

When the fluid routing plug 116 is installed within the horizontal bore106, the first and second seal 374 and 376 tightly engage thecorresponding first and second sealing surfaces 370 and 372, as shown inFIGS. 70 and 71 . During operation, the first and second seals 374 and376 wear against the first and second sealing surfaces 370 and 372. Ifthe first or second sealing surface 370 or 372 begins to erode, allowingfluid to leak around the fluid routing plug 116, the plug 116 may beremoved and replaced with a new plug 116. The first or second seal 374or 376 may also be replaced with a new seal, if needed.

The first groove 400 shown in FIG. 71 is wider than the second groove406 shown in FIG. 70 . As described below, each groove 400 and 406 issized to correspond with the size of the seal installed within thegroove. In alternative embodiments, the first and second grooves may bewider or narrower than those shown in the figures in order toaccommodate the size of the seal installed within the groove.

As discussed above, the fluid routing plug 116 may repeatedly stretchand contract in response to the changing fluid pressure. For example,when the plunger 290 is retracted out of the housing 104, the fluidpressure at the first surface 318 is equal or approximately equal to thepressure of fluid delivered to the housing 104 from the intake manifolds166 and 168. Such fluid pressure may be around 100-200 psi, for example.When the plunger 290 extends into the housing 104, the fluid at thefirst surface 318 may be pressurized to around 10,000 psi, for example.

The first seal 374, being positioned adjacent the first surface 318 ofthe fluid routing plug 116 experiences the constant change in fluidpressure. In contrast, the second seal 376, being positioned adjacentthe second surface 320, experiences more static fluid pressure. Thefluid pressure at the second surface 320 of the fluid routing plug 116may remain at or close to 10,000 psi, for example.

Continuing with FIGS. 70 and 71 , because the first seal 374 experiencesmore pressure fluctuations during operation than the second seal 376,the first seal 374 may be more robust than the second seal 376. Forexample, the first seal 374 is larger than the second seal 376 and has agenerally square cross-sectional shape, while the second seal 376 has acircular cross-sectional shape. The first seal 374 may also have ahigher durometer value than the second seal 376. As described below,both seals 374 and 376 are bi-directional seals. In alternativeembodiments, the second seal may be of the same construction as thefirst seal.

Continuing with FIG. 71 , the first seal 374 is shown engaged with bothside walls 402 of the first groove 400. In operation, as the plunger 290extends into the housing 104, pressurized fluid pushes against the rightside of the first seal 374, helping to activate the first seal 374 andcreate a tight seal between the first seal 374 and the first sealingsurface 370. As the plunger 290 retracts from the housing 104 and thefluid pressure drops, the fluid pressure is greater on the left side ofthe first seal 374. Thus, the fluid pressure may push against the leftside of the first seal 374, helping to activate the first seal 374.Therefore, in operation, the first seal 374 may move slightly betweenits left and right side.

Continuing with FIG. 70 , the second seal 376 is shown engaged with bothside walls 408 of the second groove 406. In operation, pressurized fluidwithin the housing 104 helps to activate the second seal 376, therebycreating a tight seal between the second seal 376 and the second sealingsurface 372. Because the second seal 376 experiences primarily staticfluid pressure, the second seal 376 may not move within the secondgroove 406, as much as the first seal 374 moves within the first groove400.

Continuing with FIGS. 70 and 71 , the first seal 374 also takes upapproximately 97% of the open volume within the first groove 400.Likewise the second seal 376 takes up almost 97% of the open volumewithin the second groove 406. Normally, seals are configured to take uparound 70% of the open volume within the groove the seal is installedwithin. The remaining open volume provides space for the seal to expandand move. However, in operation, fluid and proppants can fill the openvolume and wear against the groove, eventually causing the walls of thegroove to erode. If the walls of the groove are damaged, the housing 104may need to be replaced.

By sizing the grooves 400 and 406 so that the seals 374 and 376 take upalmost all of the open volume within the corresponding grooves 400 and406, there is less room for fluid or proppants to fill any open spacewithin the grooves. Specifically, fluid and proppants are prevented fromentering any open volume on the back side of the seals 374 and 376,thereby protecting the first and second grooves 400 and 406 fromerosion. In alternative embodiments, the first seal may take less volumeof the first groove than is shown in FIG. 70 . Likewise, in alternativeembodiments, the second seal may take up less volume of the secondgroove than is shown in FIG. 71 . The other grooves formed in thehousing and described herein may also be configured so that thecorresponding seals take up approximately 97% of the open volume withinthe groove.

Continuing with FIG. 71 , the first sealing surface 370 may extend up toimmediately adjacent the first surface 318 of the body 316. A firstportion 412 of the intermediate surface 322 between the first bevel 378and the first sealing surface 370 faces the housing 104 walls. A verysmall gap exists between the first portion 412 and the housing 104. Thegap may be as small as 0.001 inches in width. Such gap providesclearance to reduce friction between the fluid routing plug 116 and thehousing 104 during installation and operation. Such gap also providesspace for excess proppant to collect during operation.

Continuing with FIG. 70 , a second portion 416 of the intermediatesurface 322 between the second sealing surface 372 and the secondsurface 320 may face the walls of the housing 104. A third portion 418of the intermediate surface 322 between the second sealing surface 372and the transition bevel 386 may also face the walls of the housing 104.Like the first portion 412, a very small gap exists between the secondand third portions 416 and 418 and the housing 104. The gaps may be assmall as 0.001 inches in width. Such gaps provide clearance to reducefriction between the fluid routing plug 116 and the housing 104 duringinstallation and operation. Such gaps also provide space for excessproppant to collect during operation.

Turning back to FIG. 65 , as discussed above, the walls of the housing104 surrounding the horizontal bore 106 are sized to allow for easyinstallation of the fluid routing plug 116. The second groove 406 has adiameter D1. A maximum diameter of the second beveled surface 384 has adiameter D2. A maximum diameter of the first beveled surface 380 has adiameter D3, and the first groove 400 has a diameter D4. The diameter D4is greater than the diameter D3. The diameter D3 is greater than thediameter D2, and the diameter D2 is greater than the diameter D1.

With reference to FIGS. 72-76 and 85-89 , the suction and dischargevalves 292 and 294 are generally identical, with the exception that thedischarge valve 294 may be larger in size than the suction valve 292. Asdiscussed above, the suction and discharge valves 292 and 294 each havea sealing element 346 and 360. The sealing elements 346 and 360 eachinclude a sealing surface 420 and 422 that tapers at an angle thatmatches the angle of the tapered wall 340 and 356 of the fluid routingplug 116. Thus, the sealing surfaces 420 and 422 each taper at an angleof 30 or 45 degrees. Preferably, the tapered walls 340 and 356 and thesealing surfaces 420 and 422 both taper at an angle of 45 degrees.

Forming the mating tapered walls 340 and 356 and sealing surfaces 420and 422 at 45 degrees provides more surface area for the valves 292 and294 to seal against the fluid routing plug 116. Providing more sealingsurface area or a larger “strike face” helps distribute the forcesapplied to the valves 292 and 294 and the fluid routing plug 116,thereby providing more evenly distributed sealing. Providing more evenlydistributed sealing prevents certain areas from wearing faster thanothers, helping to increase the life of the parts.

Each valve 292 and 294 also has an outer sealing diameter A and an innersealing diameter B, as shown in FIGS. 72 and 85 . The ratio of the outersealing diameter A to the inner sealing diameter B is preferably 1.55 orgreater. This ratio helps increase the life of the valves 292 and 294and reduce any turbulent fluid flow during operation. The valves 292 and294 and the fluid routing plug 116 are configured so that no portion ofthe valves 292 and 294 enters the first or second fluid passages 326 and336 during operation. Additionally, no portion of the valve 292 entersthe blind bore 328 during operation. Rather, the suction valve 292 isconfigured only to cover the entrance 342 of the blind bore 330 on thefirst surface 318, and the discharge valve 294 is configured only tocover the openings 364 of the second fluid passages 336 on the secondsurface 320.

Continuing with FIGS. 72-76 , the suction valve 292 is shown in moredetail. The suction valve 292 comprises the sealing element 346 joinedto a stem 424. When the suction valve 292 is installed within thehorizontal bore 106, the stem 424 extends along an axis that is parallelto or aligned with central the longitudinal axis 114 of the housing 104.

The sealing element 346 comprises opposed first and second surfaces 426and 428 joined by the sealing surface 420. A groove 430 is formed in thesealing surface 420 adjacent the first surface 426, as shown in FIG. 76. A seal 432 is installed within the groove 430. The groove 430 ischaracterized by a first sidewall 434 joined to a second sidewall 436.The sidewalls 434 and 436 may be joined by an inner groove 438. Thegroove 430 is sized to correspond with the inward facing surface of theseal 432. An outward facing surface of the seal 432 comprises a convexsurface 440 joined to a concave surface 442. The seal 432 is preferablymade of a polyurethane compound. In alternative embodiments, the sealmay be made of a different elastomer material.

When the suction valve 296 seals against the first surface 318 of thefluid routing plug 116, the seal 432 and a portion of the sealingsurface 420 mate with the tapered wall 340, as shown in FIG. 51 . Theseal 432 is shaped so that the convex surface 440 displaces into, ortoward, the concave surface 442 as the seal 432 engages the tapered wall340. This relative movement allows the shear forces to be dissipated,increasing the life of the seal 432 and the suction valve 292. If theseal 432 becomes worn and no longer seals properly, the seal 342 may beremoved and replaced with a new seal 432. In alternative embodiments,the seal and groove may have various shapes and sizes, as desired. Infurther alternative embodiments, the sealing surface may not include agroove and corresponding seal.

Continuing with FIG. 76 , the second surface 428 of the sealing element346 is sized to cover the entrance 342 of the blind bore 328, as shownin FIG. 51 . A cutout 444 is formed within the second surface 428. Thecutout 444 creates a small cavity within the second surface 428. Thecavity provides space for fluid to collect and apply pressure to thesuction valve 292. Such pressure helps force the suction valve 292 tomove axially to an open position.

Continuing with FIGS. 75 and 76 , the stem 424 projects from the firstsurface 426 of the sealing element 346. An annular void 446 is formed inthe first surface 426 and surrounds the stem 424. The first surface 426further includes a ring-shaped outer rim 448 that surrounds the annularvoid 446 and the stem 424. The outer rim 448 joins the sealing surface420. The annular void 446 reduces weight within the suction valve 292and helps orient the valve's center of gravity during operation.

An annular groove 450 is formed in the outer rim 448. The groove 450 isconfigured for receiving a bottom portion of a spring 452, as shown inFIG. 83 . As described below, a top portion of the spring 452 engageswith the suction valve guide 296, as shown in FIGS. 83 and 84 . Thespring 452 biases the suction valve 292 in the closed position.Positioning the spring 452 on the outer rim 448 helps to stabilize thesuction valve 292 during operation.

With reference to FIGS. 77-82 , the stem 424 is configured to moveaxially within the suction valve guide 296. The suction valve guide 296may also be referred to as a cage for the suction valve 292. The suctionvalve guide 296 comprises a body 454 having opposed first and secondsurfaces 456 and 458. A central passage 460 is formed within the body454 and interconnects the first and second surfaces 456 and 458. Aplurality of legs 462 extend out from the body 454 adjacent its firstsurface 456 and project downward towards its second surface 458. Thesuction valve guide 296 shown in FIGS. 77-82 has six evenly spaced legs462 formed around its body 454. In alternative embodiments, more or lessthan six legs may be formed on the body and may be non-uniformly spaced.

The legs 462 gradually decrease in thickness from the body 454 to abottom surface 464 of each leg 462. The bottom surface 464 of each leg462 is extremely thin so that the legs 462 do not block or interferewith the openings 348 of the second fluid passages 336 on the firstsurface 318, as shown in FIG. 50 .

Continuing with FIGS. 77-82 , an outer surface of each leg 462 includesa bevel 466. The bevels 466 are configured to engage a correspondingbevel 468 formed in the walls of the housing 104, as shown in FIGS. 50and 51 . The suction valve guide 296 is inserted into the horizontalbore 106 until the bevels 466 and 468 engage, allowing the guide 296 tobottom out on the walls of the housing 104. Once the bevels 466 and 468are engaged, the suction valve guide 296 is held against the walls ofthe housing 104 by the spring 452 and fluid pressure.

When the suction valve guide 296 is in its installed position, thebottom surface 464 of each of the legs 462 hovers just above the firstsurface 318 of the fluid routing plug 116, leaving a gap between thelegs 462 and the plug 116. The bottom surfaces 464 do not directlycontact the fluid routing plug 116 in order to prevent the suction valveguide 296 from applying load to the plug 116 during operation.

Continuing with FIG. 80 , a tubular insert 470 is installed within thecentral passage 460 of the body 454. The insert 470 may be press-fitwithin the passage 460. The insert 470 extends the length of the centralpassage 460 and is formed from a more wear resistant material than thesuction valve guide 296. For example, the insert 470 may be made oftungsten carbide, while the suction valve guide 296 may be made of highstrength alloy steel. The stem 424 is installed within the insert 470and reciprocates within the insert 470 during operation, as shown inFIGS. 50 and 51 . Any fluid contained within the insert 470 drains fromthe opening of the central passage 460 on the first surface 456 of thebody 454.

During operation, the stem 424 may wear against the insert 470 as itreciprocates. The insert 470 helps decrease the rate of wear and helpsthe stem to wear evenly against the insert. Forming only the insert 470out of a wear resistant material helps reduce the cost of the otherparts, that do not experience as much wear during operation.

Turning to FIGS. 83 and 84 , the spring 452 is interposed between thesuction valve 292 and the suction valve guide 296. The spring 452 isheld between the outer rim 448 of the suction valve 292 and an innersurface 472 of the legs 462. At least a portion of the spring 452surrounds the body 454 of the suction valve guide 296. As the suctionvalve 292 moves to an open position, the spring 452 compresses betweenthe suction valve 292 and the suction valve guide 296.

With reference to FIGS. 85-89 , the discharge valve 294 is shown in moredetail. As discussed above, the discharge valve 294 is constructedidentically to the suction valve 292, with the exception that thedischarge valve 294 may be larger in size. The discharge valve 294 shownin FIGS. 85-89 , for example, has a larger sealing surface 422 and alonger stem 474 than the suction valve 292. When the discharge valve 294is installed within the horizontal bore 106, the stem 424 extends alongan axis that is parallel to or aligned with the central longitudinalaxis 114 of the housing 104. A seal 475 is installed within a groove 477formed in the sealing surface 422 and is configured to engage with thetapered wall 356 formed in the second surface 320 of the fluid routingplug 116. A bottom surface 476 of the discharge valve 294 is sized tocover the central base 354, as shown in FIG. 50 .

With reference to FIGS. 90-95 , the stem 474 formed on the dischargevalve 294 is configured to move axially within the discharge valve guide298. The discharge valve guide 298 may also be referred to as a cage forthe discharge valve 294. The discharge valve guide 298 comprises a body478 having opposed first and second surfaces 480 and 482 joined by anintermediate surface 484. The intermediate surface 484 includes a frontportion 486, a medial portion 488, and a rear portion 490. The medialportion 488 has a larger diameter than both the front and rear portions486 and 490. The front portion 486 has a slightly larger diameter thanthe rear portion 490.

Continuing with FIGS. 90-95 , a blind bore 492 is formed in the firstsurface 480 and extends into the front portion 486 of the body 478. Theblind bore 492 is configured to receive a tool used to grip thedischarge valve guide 298. The front portion 486 is sized to be receivedwithin the cutout 308 formed in the retainer 300, as shown in FIGS. 50and 51 . When the discharge valve guide 298 and the retainer 300 areengaged, the blind bore 492 opens into the central passage 310 formed inthe retainer 300.

A central passage 494 is formed in the body 478 and opens on the secondsurface 482, as shown in FIGS. 93 and 94 . The central passage 494 opensin the body 478 into an axially blind counterbore 496. A plurality ofrelief ports 498 are formed in the body 478. Each relief port 498interconnects the counterbore 496 and a base 500 of the medial portion488, as shown in FIG. 94 .

Continuing with FIGS. 93 and 94 , a tubular insert 502 is installedwithin the central passage 494. The insert 502 is identical to theinsert 470, with the exception that the insert 502 may be larger thanthe insert 470. During operation, the stem 474 moves axially within theinsert 502 installed within the central passage 494. Any fluid withinthe insert 502 drains from the body 478 through the counterbore 496 andthe relief ports 498.

Continuing with FIGS. 90-92 , a plurality of legs 504 project from themedial portion 488 and extend towards the second surface 482 of the body478. The discharge valve guide 298 shown in FIGS. 90-95 comprises fivelegs 504. The legs 504 are positioned on the body 478 so as to leave alarge space 506 between at least two adjacent legs 504. Other than thespace 506, the legs 504 are equally spaced from one another. The space506 is intended to align with the discharge bore 178, thereby preventingany legs 504 from blocking the discharge bore 178 during operation.Providing the space 506 therefore allows fluid to flow freely betweenthe discharge valve 294 and the discharge bore 178 without significantobstructions. The space 506 also helps minimize wear applied to the legs504 by the flowing fluid over time. In alternative embodiments, the bodymay have more or less than five legs and be spaced, as desired, as longas the legs are positioned on the body so as to leave a large spacebetween at least two of the legs.

With reference to FIG. 90 , each of the legs 504 has a thicker upperportion 508 and thinner lower portion 510. The thicker upper portion 508provides strength to the legs 504 while the lower portion 510 is thinnedin order to provide more room for fluid flow around the legs 504. Theupper portion 508 also includes a tapered inner surface 512. Taperingthe inner surface 512 of the legs 504 provides strength and alleviatesstress in the legs 504 during operation.

Continuing with FIGS. 90-95 , when the discharge valve guide 298 isinstalled within the horizontal bore 106, a bottom surface 514 of eachleg 504 engages the outer rim 352 of the second surface 320 of the fluidrouting plug 116, as shown in FIGS. 50 and 51 . The discharge valveguide 298 is held against the fluid routing plug 116 by the retainer300. Such engagement helps keep the second bevel 382 of the fluidrouting plug 116 seated against the second beveled surface 384, as shownin FIGS. 65 and 68 .

Continuing with FIGS. 93 and 95 , a dowel pin 516 is installed within ablind bore 517 formed in the medial portion 488 of the body 478. Thedowel pin 516 is configured to be received within a dowel pin hole orgroove 518 formed in the walls of the housing 104 surrounding thehorizontal bore 106, as shown in FIGS. 96 and 97 . The discharge valveguide 298 is installed within the horizontal bore 106 such that thedowel pin 516 is positioned within the dowel pin hole 518. Suchpositioning ensures that the space 506 between the pair of legs 504aligns with the discharge bore 178, thus preventing any legs 504 fromblocking the discharge bore 178 during operation.

Continuing with FIGS. 96 and 97 , a seal 520 is interposed between theintermediate surface 484 of the body 478 and the walls of the housing104. The seal 520 may be identical to the second seal 376 shown in FIGS.65 and 70 . In alternative embodiments, the seal may be identical to thefirst seal 374 shown in FIGS. 65 and 71 . The seal 520 is installedwithin a groove 522 formed in the housing 104. The groove 522 ischaracterized by two sidewalls 524 joined to a base 526. The sidewalls524 may join the base 526 via radius corner or at a 90 degree angle.During operation, the seal 520 wears against the outer intermediatesurface 484 of the discharge valve guide 298. If the intermediatesurface 484 begins to erode, allowing fluid to leak around the seal 520,the discharge valve guide 298 may be removed and replaced with a newdischarge valve guide 298.

With reference to FIGS. 98 and 99 , a spring 528 is installed betweenthe discharge valve 294 and the discharge valve guide 298. A bottomportion of the spring 528 sits in a groove 530, shown in FIG. 89 ,formed in an outer rim 532 of the discharge valve 294. A top portion ofthe spring 528 engages a ledge 534 formed in the base 500 of the medialportion 488 of the discharge valve guide 298. During operation, thespring 528 compresses against the ledge 534 of the medial portion 488.

Turning to FIG. 100 , the components installed within the housing 104are installed through the first surface 108, starting with the suctionvalve guide 296. The diameter of the installed components slightlyincreases from the second surface 320 to the first surface 318. Forexample, the suction valve guide 296 has smaller outer diameters thanthe fluid routing plug 116, and the fluid routing plug 116 has smallerouter diameters than the discharge valve guide 298. The discharge valveguide 298 has smaller outer diameters than the retainer 300.

Likewise, the diameters of the walls surrounding the horizontal bore 106generally increase from the second surface 110 to the first surface 108.As shown in FIG. 100 , a diameter D4 of the horizontal bore 106 isgreater than a diameter D3 of the horizontal bore 106. The diameter D3of the horizontal bore 106 is greater than a diameter D2 of thehorizontal bore 106. The diameter D2 of the horizontal bore 106 isgreater than a diameter D1 of the horizontal bore 106. Such constructionallows the components to be installed without engaging the walls of thehousing 104 until the component is at its intended installed position.The seals 374, 376, and 520 may be installed within the housing 104prior to installing the other components described above.

Turning to FIGS. 100A-100E, another embodiment of a fluid routing plug550 is shown. The fluid routing plug 550 may be installed within thehousing 104 in place of the fluid routing plug 116. The fluid routingplug 550 is identical to the fluid routing plug 116, with a fewexceptions. The fluid routing plug 550 comprises a body 552 having afirst outer surface 554 joined to a second outer surface 556 by anintermediate outer surface 558. The second surface 556 of the fluidrouting plug 550 is generally identical to the second surface 320 of thefluid routing plug 116, but a central base 560 formed in the secondsurface 556 is spaced from an edge 562 of a tapered wall 564 formed inthe second surface 556. The central base 560 is spaced from the taperedwall 564 such that a throat 566 is formed between the central base 560and the tapered wall 564.

Continuing with FIGS. 100A-100D, a blind hole 568 is formed in thecentral base 560 and a plurality of openings 570 corresponding to aplurality of second fluid passages 572 open on the central base 560 andsurround the blind hole 568. In operation, fluid exiting the openings570 flows into the throat 566 before pushing against the discharge valve294 engaged with the second surface 556. Allowing fluid to gather in thethroat 566 before contacting the discharge valve 294 helps the fluid tocontact more surface area of the discharge valve 294, instead of havinga plurality of single points of contact from each second fluid passageopening. Allowing the fluid to contact more surface area of thedischarge valve 294 helps reduce wear to the valve over time.

Continuing with FIGS. 100E and 100F, the intermediate surface 558 of thefluid routing plug 550 is identical to the intermediate surface 322formed on the fluid routing plug 116. However, the intermediate surface558 may include a cutout 576 adjacent the second surface 556. The cutout576 provides space for fluid or proppant to collect during operation, asshown in FIG. 100F. The cutout 576 also helps reduce friction duringinstallation of the fluid routing plug 550 within the housing 104. Asmall gap 578 may also exist between the walls of the housing 104 andthe intermediate surface 558 between a second sealing surface 580 andthe cutout 576, as shown in FIG. 100F. The gap 578 helps the seal 376breath during operation.

Continuing with FIG. 100B, the first surface 554 of the fluid routingplug 550 is identical to the first surface 318 of the fluid routing plug116, with the exception of its outer rim 582. The outer rim 582 is flatand wider than the outer rim 338, shown in FIG. 55 . Because the outerrim 582 is wider, a plurality of openings 584 for the second fluidpassages 572 may have a slightly larger diameter than the openings 348,shown in FIG. 56 . Likewise, the openings 570 may also have a slightlylarger diameter than the openings 364 shown in FIG. 54 . Providing aslightly larger diameter for the second fluid passages 572 helps reducefluid velocity through the fluid routing plug 550 during operation.Reducing fluid velocity within the fluid routing plug 550 helps reducewear to the fluid routing plug 550 over time.

Turning to FIGS. 101-109 , another embodiment of a fluid routing plug600 is shown. The fluid routing plug 600 may be installed within thehousing 104 in place of the fluid routing plug 116. The fluid routingplug 600 is identical to the fluid routing plug 116, with a fewexceptions. The fluid routing plug 600 comprises a body 602 having afirst outer surface 604 joined to a second outer surface 606 by anintermediate outer surface 608. In contrast to the fluid routing plug116, the first and second surfaces 604 and 606 of the fluid routing plug600 are configured so that each surface 604 and 606 has identicallysized tapered walls 610 and 612, as shown in FIG. 103 . Because thetapered walls 610 and 612 are the same size, a suction valve 614 and adischarge valve 616 used with the fluid routing plug 600 may beidentical in size, as shown in FIGS. 108 and 109 .

Using the same size suction and discharge valves 614 and 616 helpsequalize the forces applied to the fluid routing plug 600 and the valves614 and 616 during operation, helping to reduce any wear to the partsover time. Making the suction and discharge valves 614 and 616 identicalalso makes replacing the valves 614 and 616 during operation easier.

Continuing with FIGS. 103, 105, and 106 , the tapered wall 612 formed inthe second surface 606 extends between an outer rim 618 and an annulargroove 620 formed in the center of the second surface 606. The annulargroove 620 may be considered a central base formed in the second surface606. The groove 620 surrounds a blind bore 622 formed in the center ofthe second surface 606. The blind bore 622 is identical to the blindbore 362 formed in the fluid routing plug 116, as shown in FIG. 55 .

The groove 620 is characterized by two parallel sidewalls 624 joined bya base 626. The sidewalls 624 each extend at a non-zero angle relativeto a central longitudinal axis 628 of the body 602. Because thesidewalls 624 of the groove 620 extend at an angle, the base 626 of thegroove 620 extends at a non-zero angle relative to the centrallongitudinal axis 628 of the body 602. Preferably, the base 626 extendsat approximately the same angle as the tapered wall 612 so that the base626 and the tapered wall 612 are in a generally parallel relationship.The tapered wall 612 shown in FIG. 103 extends at a 45 degree anglerelative to the central longitudinal axis 628.

An annular inner edge 638 of the tapered wall 612 is joined to the outersidewall 624 of the groove 620 at a right angle. The diameter of theinner edge 638 of the tapered wall 612 is the same size as a diameter ofan entrance 630 of an axially blind bore 632 formed in the first surface604, as shown in FIG. 103 . In alternative embodiments, the grooveformed in the second surface and the inner edge of the tapered wall maynot have an annular shape.

Continuing with FIGS. 103, 105, and 106 , a plurality of second fluidpassages 634 are formed in the body 602. The second fluid passages 634are identical to the second fluid passages 336 formed in the fluidrouting plug 116, shown in FIGS. 52-64 , with the exception of thepositioning of their openings 636 on the second surface 606. Each secondfluid passage 634 opens on the base 626 of the groove 620 formed in thesecond surface 606. Thus, the openings 636 are axially spaced from theinner edge 638 of the tapered wall 612. Because the sidewalls 624 of thegroove 620 are formed at an angle, the inner edge 638 of the taperedwall 612 slightly overlaps the openings 636, as shown in FIG. 106 . Bypositioning the openings 636 in an axially spaced relationship with theinner edge 638 of the tapered wall 612, the size of the tapered wall 612can be decreased without decreasing the size of the openings 636.

Because the tapered wall 612 is decreased in size from the tapered wall356 shown in FIG. 55 , the outer rim 618 on the second surface 606 iswider than the outer rim 352. The outer rim 618 also tapers between theintermediate surface 608 and the tapered wall 612, as shown in FIGS. 103and 104 . Such taper increases the length of the tapered wall 612without increasing the length of the intermediate surface 608.

Continuing with FIGS. 101-107 , the first surface 604 is identical tothe first surface 318 shown in FIGS. 53, 55, and 56 , with the exceptionof its outer rim 640. Instead of tapering like the outer rim 338, shownin FIG. 55 , the outer rim 640 is flat. The outer rim 640 is flat inorder to slightly decrease the size of the tapered wall 610 to match thesize of the tapered wall 612. The intermediate surface 608 of the fluidrouting plug 600 is identical to that of the fluid routing plug 116,shown in FIG. 64 . A plurality of first fluid passages 642 formed in thebody 602 are identical to the first fluid passages 326, shown in FIGS.55, 57, and 59 . The second fluid passages 634 open on the outer rim 640of the first surface 604, as shown by the openings 644. The openings 644are positioned in groups 645, in the same manner as the second fluidpassages 336 formed in the fluid routing plug 116, as shown in FIG. 56 .The openings 636 on the second surface 606 may remain spaced in groups645, as shown in FIG. 106 .

With reference to FIGS. 108 and 109 , the fluid routing plug 600 routesfluid throughout the housing 104 in the same manner as the fluid routingplug 116. The suction valve guide 296 is shown engaged with suctionvalve 614. Another embodiment of a discharge valve guide 647 is shownengaged with the discharge valve 616.

The discharge valve guide 647 is identical to the discharge valve guide298, shown in FIGS. 90-95 , with a few exceptions. A counterbore 649formed in the guide 647 is larger than the counterbore 496. Thecounterbore 649 is larger in order to accommodate the shorter stem 646of the discharge valve 616. An insert 651 installed within the dischargevalve guide 647 is the same size as the insert 470 installed within thesuction valve guide 296.

With reference to FIGS. 110-114 , as discussed above, in contrast to thevalves 292 and 294, the valves 614 and 616 are identical in size andshape. The valves 614 and 616 are generally identical to the valves 292and 294, with a few exceptions. Each valve 614 and 616 comprises asealing element 652 joined to a stem 646. The stem 646 projects from afirst surface 650 of the sealing element 652.

An annular cutout 648 is formed within a medial portion of the stem 646.The cutout 648 provides space for fluid or proppants to collect duringoperation. Providing such space prevents the fluid and proppants fromrubbing against the inserts 470 and 502. The suction and dischargevalves 292 and 294 may be configured to include an annular cutout withintheir stems 424 and 474.

Continuing with FIGS. 110-114 , the sealing element 652 further includesa second surface 668 joined to the first surface 650 by a sealingsurface 658. A groove 656 is formed in the sealing surface 658 forhousing a seal 654. The groove 656 is identical to the groove 430, shownin FIG. 76 . An outward facing surface of the seal 654 comprises asidewall 660 joined to a tapered base 662. In operation, the taperedbase 662 engages the tapered walls 610 and 612 of the fluid routing plug600. The sidewall 660 may compress creating a tight seal.

The first surface 650 of the sealing element 652 includes an outer rim664. An outer ledge 666 surrounds the outer rim 664. A bottom portion ofa spring engages the outer rim 664 and is held in place by the outerledge 666. While not shown, a cutout may be formed in the second surface668 of the sealing element 652, like the cutout 444, shown in FIG. 76 .

With reference to FIGS. 115-117 , an alternative embodiment of a fluidrouting plug 700 is shown. The fluid routing plug 700 may be installedwithin the housing 104 in place of the fluid routing plug 116. The fluidrouting plug 700 is identical to the fluid routing plug 116, with theexception of the shape of its first and second bevels 702 and 704. Whenthe fluid routing plug 700 is first installed within the horizontal bore106, the second bevel 704 only partially engages a second beveledsurface 706, as shown in FIG. 116 . The bevels 704 and 706 mate at asecond bevel mating surface 708 and a second beveled surface matingsurface 710. Below the mating surfaces 708 and 710, the second bevel 704and the second beveled surface 706 have mating angles that are notequal, causing a gap 712 to exist between the bevels 704 and 706.Specifically, the second bevel 704 may have a slightly convex shape sothat portions of the second bevel 704 don't match the flat shape of thesecond beveled surface 706.

The width of the gap 712 gradually increases between the mating surfaces708 and 710 and a bottom portion 714 of the second bevel 704 and abottom portion 716 of the second beveled surface 706. Thus, the width Bof the gap 712 is wider than the width A of the gap 712. Because thesecond bevel 704 has a slightly convex shape, the angle between themating surfaces 708 and 710 is different from the angle between thebottom portions 714 and 716.

Turning to FIG. 117 , the first bevel 702 and the first beveled surface718 are shown in more detail. Like the second bevel 704, the first bevel702 may only partially engage a first beveled surface 718. The bevels702 and 718 mate at a first bevel mating surface 720 and a first beveledsurface mating surface 722. Below the mating surfaces 720 and 722, thefirst bevel 702 and the first beveled surface 718 have mating anglesthat are not equal, causing a gap 724 to exist between the bevels 702and 718. Specifically, the first bevel 702 may have a slightly convexshape so that portions of the first bevel 702 do not match the flatshape of the first beveled surface 718.

The width of the gap 724 gradually increases between the mating surfaces720 and 722 and a bottom portion 726 of the first bevel 702 and a bottomportion 728 of the first beveled surface 718. Thus, the width B of thegap 724 is wider than the width A of the gap 724. Because the firstbevel 702 has a slightly convex shape, the angle between the matingsurfaces 720 and 722 is different from the angle between the bottomportions 726 and 728.

The width of the gaps 712 and 724 has been exaggerated in FIGS. 116 and117 for illustration purposes. In reality, portions of the gaps 712 and724 may be approximately 0.002 inches in width, for example. However,the gaps 712 and 724 may be wider or smaller depending on the materialsand forces used.

As discussed above, in operation, the fluid pressure applied to thefluid routing plug 700 will cause the plug 700 to compress and expand asthe plunger 290 retracts from the housing 104. As the fluid routing plug700 starts to expand, the bottom portion 714 of the second bevel 704will move to engage the bottom portion 714 of the second beveled surface706, causing the bottom portions 714 and 716 to mate. Likewise, thebottom portion 726 of the first bevel 702 will move to engage the bottomportion 728 of the first beveled surface 718. Such movement of the fluidrouting plug 700 distributes the load applied to the fluid routing plug700 through the length of the first and second bevels 702 and 704.

With reference to FIGS. 118-120 , an alternative embodiment of a fluidrouting plug 800 is shown. The fluid routing plug 800 may be installedwithin the housing 104 in place of the fluid routing plug 116. The fluidrouting plug 800 is identical to the fluid routing plug 700, with theexception of the shape of its first and second bevels 802 and 804. Likethe fluid routing plug 700, the second bevel 804 is sized to leave a gap806 between the second bevel 804 and a second beveled surface 808 whenthe fluid routing plug 800 is first installed within the housing 104. Incontrast to the gap 712, an angle formed between the mating surfaces 810and 812 and bottom portions 814 and 816 of the second bevel 804 andsecond beveled surface 808 remains the same. Thus, an area A of the gap806 has the same angle as an area B of the gap 806.

Likewise, the first bevel 802 is shaped so that an angle formed betweenthe first bevel 802 and a first beveled surface 820 stays relatively thesame between mating surfaces 822 and 824 and bottom portions 826 and828. Thus, the width A of the gap 818 has approximately the same angleas the width B of the gap 818.

The width of the gaps 806 and 818 has been exaggerated in FIGS. 119 and120 for illustration purposes. In reality, portions of the gaps 806 and818, for example, may be approximately 0.002 inches in width. However,the gaps 806 and 818 may be wider or smaller depending on the materialsand forces used.

As discussed above, the first and second bevels 802 and 804 expandduring operation. Such movement of the fluid routing plug 800distributes the load applied to the fluid routing plug 800 through thelength of the first and second bevels 802 and 804.

In alternative embodiments, the first bevel may be configured to have agap that increases in size, as shown in FIG. 117 , while the secondbevel may be configured to have a gap that increases by a differentamount, as shown in FIG. 119 , and vice versa. In further alternativeembodiments, the width of the gap may be of various shapes and sizesdepending on the materials used and forces involved. In even furtheralternative embodiments, the intermediate surface of the fluid routingplug may include any combination of the different bevel constructionsdescribed herein.

In contrast to the first fluid passages 326, shown in FIGS. 55 and 58 ,a longitudinal axis 914 of each first fluid passage 910 does notintersect a central longitudinal axis 916 of the body 902, as shown inFIG. 125 . Rather, the first fluid passages 910 are formed such that thelongitudinal axis 914 of each passage 910 is offset from the centrallongitudinal axis 916 of body 902. The offset configuration of the firstfluid passages 910 encourages a vortex type flow of fluid about thecentral longitudinal axis 916, thereby reducing fluid turbulence duringoperation. In alternative embodiments, the longitudinal axis 914 of eachfirst fluid passage 910 may intersect the longitudinal axis 916 of thebody 902.

A plurality of openings 918 formed on the intermediate surface 908 forthe first fluid passages 910 are similar to the openings 334, shown inFIGS. 57 and 59 , but have a more oblong shape, as shown in FIG. 121 .The oblong shape shown in FIG. 121 has opposed first and second ends 920and 922. The second end 922, which is closer to the second surface 906,is slightly wider than the first end 920. The unequal size of the ends920 and 922 helps direct fluid along the offset longitudinal axis 914 ofthe first fluid passages 910. The unequal size of the ends 920 and 922also helps increase the wall thickness in certain areas of the body 902between the first fluid passages 910 and a plurality of second fluidpassages 924.

In alternative embodiments, the opposed ends of the openings may beidentical in size or may be shaped identical to the openings 334, shownin FIGS. 57 and 59 . The opening 918 of the first fluid passage 910shown in FIG. 121 extends along an axis that is parallel to thelongitudinal axis 916 of the body 902. In alternative embodiments, theopenings of the first fluid passages may extend at a non-zero anglerelative to the longitudinal axis 916 of the body 902, as shown forexample by the openings 972 shown in FIG. 128D. The angle at which thefirst fluid passages 910 are formed in the body 902 may vary, asdesired, in order to increase the wall thickness within the body 902 andreduce stress in the body 902 during operation.

Continuing with FIGS. 122 and 126 , each of the second fluid passages924 formed in the body 902 interconnects the first and second surfaces904 and 906. The second fluid passages 924 are identical to the secondfluid passages 336, shown in FIGS. 60-63 , but the second fluid passages924 are slightly pivoted from the position of the second fluid passages336. Each second fluid passage 924 is pivoted so that it has a compoundangle with respect to the central longitudinal axis 916, as shown inFIGS. 122, 123 126, and 127. Meaning, each second fluid passage 924extends such that it has two different angles relative to the centrallongitudinal axis 916—up-and-down, and side-to-side. Like the firstfluid passages 910, forming the second fluid passages 924 at such anglesencourages a vortex type flow of fluid about the central longitudinalaxis 916, thereby reducing fluid turbulence during operation.

Continuing with FIGS. 124, 127, and 128 , the first surface 904 of thefluid routing plug 900 may be identical to the first surface 318, shownin FIGS. 53, 55, and 56 . However, an outer rim 926 of the first surface904 may be flat rather than tapered. The second surface 906 of the fluidrouting plug 900 is identical to the fluid routing plug 116, but acentral base 928 formed in the second surface 906 may be slightly setback within the body 902, as compared to the central base 354, shown inFIGS. 54 and 55 . An outer rim 930 on the second surface 906 may beslightly wider than the outer rim 352, shown in FIGS. 54 and 55 . Theintermediate surface 908 of the fluid routing plug 900 may be identicalto the intermediate surface 322 of the fluid routing plug 116.Alternatively the intermediate surface may be identical to those formedon the fluid routing plug 700 or 800.

In alternative embodiments, the first and second surfaces 904 and 906 ofthe fluid routing plug 900 may be configured so that its tapered walls932 and 934 are the same size, like the fluid routing plug 600. Infurther alternative embodiments, the first and second surfaces of thefluid routing plug 900 may be identical to the first and second surfacesof the fluid routing plug 116.

Turning to FIGS. 128A-128G, another embodiment of a fluid routing plug950 is shown. The fluid routing plug 950 may be installed within thehousing 104 in place of the fluid routing plug 116. The fluid routingplug 950 is identical to the fluid routing plug 900, with a fewexceptions. The fluid routing plug 950 comprises a body 962 having afirst outer surface 964 joined to a second outer surface 952 by anintermediate outer surface 966. In contrast to the fluid routing plug900, the second surface 952 of the fluid routing plug 950 is formedidentically to the second surface 856 of the fluid routing plug 850,shown in FIGS. 100A-100E. A central base 954 formed in the secondsurface 952 is spaced from an edge 956 of a tapered wall 958 such that athroat 960 is formed within the second surface 952. The throat 960serves the same purpose as the throat 566 formed in the fluid routingplug 550.

Continuing with FIG. 128A-128G, a plurality of first fluid passages 968,shown in FIG. 128G, and a plurality of second fluid passages 970, shownin FIG. 128A, are formed in the body 962. The first and second fluidpassages 968 and 970 are identical to the first and second passages 910and 924 formed in the fluid routing plug 900. However, as discussedabove, an opening 972 of the first fluid passages 968 may extend along anon-zero angle relative to a central longitudinal axis 974 of the body962, as shown in FIG. 128D. In alternative embodiments, the openings 972may be identical to the openings 918, shown in FIG. 121 . Like the fluidrouting plug 900, the angle at which the first fluid passages 968 areformed in the body 962 may vary, as desired, in order to increase thewall thickness within the body 962 and reduce stress in the body 962during operation.

In alternative embodiments, the first and second surfaces 964 and 952 ofthe fluid routing plug 950 may be configured like the fluid routing plug600. In further alternative embodiments, the first and second surfacesof the fluid routing plug 950 may be identical to the first and secondsurfaces of the fluid routing plug 116.

Turning to FIGS. 129-131 , another embodiment of a fluid routing plug1000 is shown. The fluid routing plug 1000 may be installed within thehousing 104 in place of the fluid routing plug 116. The fluid routingplug 1000 is identical to the fluid routing plug 116, but includes afirst and second annular recess 1002 and 1004 formed in its intermediatesurface 1001. The first annular recess 1002 is positioned between afirst bevel 1006 and a first sealing surface 1008. The second annularrecess 1004 is positioned between a second sealing surface 1010 and asecond bevel 1012.

When the fluid routing plug 1000 is installed within the horizontal bore106, a small annular space exists between the wall of the housing 104and each recess 1002 and 1004. The space provides relief areas forexcess fluid or proppant to collect during operation. The first andsecond recesses 1002 and 1004 may also be formed in the intermediatesurfaces of the fluid routing plugs 550, 600, 700, 800, 900, and 950.

In alternative embodiments, the first and second surfaces of each of thefluid routing plugs 550, 600, 700, 800, 900, and 950 may each be sizedso as to engage with identically sized suction and discharge valves 292,294, 614 or 616, as discussed with regard to fluid routing plug 600. Infurther alternative embodiments, the first and second surfaces of eachof the fluid routing plugs 550, 600, 700, Boo, 900, and 950 may be sizedso as to engage with differently sized suction and discharge valves 292,294, 614 or 616. In such embodiment, the valves 292, 294, 614 or 616 maybe sized as desired, as long as the ratio of the outer sealing diameterA to the inner sealing diameter B of each valve is preferably 1.55 orgreater, as discussed with regard to FIGS. 72 and 85 . The desired sizeof the valve may vary depending on the desired fluid velocity within thecorresponding fluid routing plug.

One or more kits may be useful in assembling the fluid end section 102.A kit may comprise a plurality of housings 104 and a plurality of thecorresponding fluid routing plugs 116, 550, 600, 700, 800, 900, or 950.The kit may also comprise a plurality of suction valves 292 or 614,discharge valves 294 or 616, suction valve guides 296, discharge valveguides 298 or 657, springs 452 and 528, retainer 300, stuffing box 140,retainer 232, plunger packing 224, packing nut 276, fastening system234, discharge conduit 174, and the various seals described herein. Thekit may also comprise the intake manifolds 166 and 168, pipe system 176,connect plate 118, fastening system 146 and stay rods 120. The kit mayalso comprise other various features described herein for use with thefluid end 100. Unless specifically described herein, the variouscomponents of the fluid end 100 may be made of high strength alloysteel, such as carbon steel or stainless steel.

The concept of a “kit” is described herein due to the fact that fluidends are often shipped or provided unassembled by a manufacturer, withthe expectation that a customer will use components of the kit toassemble a functional fluid end. Alternatively, some components arereplaced during operation. Accordingly, certain embodiments within thepresent disclosure are described as “kits,” which are unassembledcollections of components. The present disclosure also describes andclaims assembled apparatuses and systems by way of reference tospecified kits, along with a description of how the various kitcomponents are actually coupled to one another to form the apparatus orsystem.

The term “means for routing fluid” refers to the various fluid routingplugs described herein and structural equivalents thereof. The term“means for regulating fluid flow” refers to the various suction anddischarge valves and suction and discharge valve guides described hereinand structural equivalents thereof. A “means for pressurizing fluid”refers to the fluid end and the various embodiments of housings andcomponents installed within or attached to the various housingsdescribed herein and structural equivalents thereof.

While not shown herein, one of skill in the art will appreciate that thefluid end 100 described herein may be formed as a single housing havinga plurality of horizontal bores formed therein and positioned in aside-by-side relationship. The housing may be attached to a single,large connect plate. In further alternative embodiments, the singlehousing described above may be broken up into one or more sections havetwo or more horizontal bores formed therein. Such housings may beattached to one or more connect plates.

One of skill in the art will further appreciate that various features ofthe fluid routing plugs, housings, and other components described hereinmay be modified or changed, as desired. While not specifically shown ina figure herein, various features from one or more of the fluid routingplugs described herein may be included in another one of the plugs.Likewise, various features from one or more of the different housingsdescribed herein may be included in another one of the housings.

Power End 103

Referring now to FIGS. 132-190 , the power end 103 disclosed hereinincludes some or all of the following features and advantages in variousembodiments:

-   -   Modular construction of the power end includes individual        connect plates, individual crosshead frames, and/or individual        crosshead assemblies that may be individually replaced, which        allows failed components to be replaced without discarding other        components.    -   The power end assembly is held together by one or more sets of        stay rods that may be disengaged and reengaged using nuts to        facilitate replacement of components without cutting or welding.    -   Tension on the one or more sets of stay rods causes compression        on the power end assembly to preload the power end assembly        against working loads and/or to apply compression to components        made of materials that benefit from compression.    -   Using a plurality of sets of stay rods enables the stay rods to        be vertically offset such that deflection and stress from        driving the fluid end can be reduced by moving the set of stay        rods that couple the connector section to the power end assembly        closer to the cylindrical axes of the plungers reciprocating in        the fluid ends.    -   Compression from the one or more sets of stay rods is        distributed throughout the power end using one or more unitary        plates. The one or more unitary plates also reduces stress on        and displacement of modular components due to static and working        loads.    -   Different components of the power end assembly are made of        different materials that are suited to different purposes. For        example, components housing moving components such as the        crosshead frames and crank frame may be made of ductile iron        that is being compressed by plates made of high-alloy steel.        Compressing the ductile iron components increases their        performance (e.g., resistance to wear, working life) in various        embodiments. Other components may be made of high-alloy steel        for strength. The use of different materials may also reduce        weight and cost of materials.    -   Weight is strategically reduced throughout the power end by        using individual crosshead frames and through the use of        weight-reducing features in the crosshead section, crank        section, and various plates.    -   Blind nuts and/or threaded receivers in one or more of the        plates allows nuts to be installed at the proper amount of        torque without measuring an amount of exposed thread extending        from the nuts.    -   Feet in the crank frame anchor the crank frame to the base        section at each bearing journal and in line with bearing loads        that are transferred to the feet and then to the base section.    -   Longer connecting arms and wider crossheads lower        pressure-velocity loading of the crosshead assembly on the        crosshead frames.    -   Using pony rod seal housings that hold the pony rod seal        partially inside the crosshead frame increases the clearance        around the pony rod clamp on the backstroke of the power end        assembly.    -   Lubrication is applied at the top of the power end at both the        crosshead section and the crank section, collected through a        plurality of drains in the crank section, and reused in a closed        lubrication system.    -   Spacers maintain the distance between the connect plates and the        crosshead frames.    -   Use of seals positioned in grooves cut into components instead        of gaskets avoids common problems with gaskets such as        saturation and over compression.    -   Various bores in the crosshead frames facilitate the flow of air        and lubricant from the crosshead frames to the crank section.    -   Various alignment dowel pins, countersunk holes, and/or sleeves        facilitate alignment of components during assembly (or        reassembly) of the power end assembly.

The advantages conferred by the previously described improvements arelisted here for convenience. This is not an exhaustive list and it isexpected that other benefits will be realized as the improvements areimplemented. Omission from this list does not preclude theidentification of additional benefits.

Continuing with FIGS. 132-190 , the power end 103 includes a cranksection 7122, a crosshead section 7124, a connector section 7126, adrive section 7130, and a base section 7140. For the sake of clarity, asused herein “front” or “front side” refers to portions of power end 103that are proximate to fluid end 100 along a longitudinal axis and “rear”or “rear side” refers to portions of power end 103 that are distal fromfluid end 100 along the longitudinal axis. Similarly, as used herein“top” or “top side” refers to portions of the power end 103 that aredistal from base section 7140 along a vertical axis and “bottom” or“bottom side” refers to portions of the power end 103 that are proximateto base section 7140 along the vertical axis. Accordingly, in theembodiment shown in FIGS. 132-140 , for example, connector section 7126is in front of crosshead section 7124, which in turn is in front ofcrank section 7122, and fluid end 100 and power end 103 are coupled tothe top of base section 7140. For consistency throughout this disclosureall references to longitudinal, transverse, vertical axes refer to theaxes shown in FIG. 132 . However, the axes may be defined differently,as desired.

In various embodiments, power end 103 includes crank section 7122,crosshead section 7124, and connector section 7126. Crank section 7122is configured to receive rotational motion (e.g., from drive section7130). As discussed herein, crank section 7122 includes a crank frame(e.g., crank frame 7210 shown in FIG. 133 ), a crankshaft (e.g.,crankshaft 7212 shown in FIG. 133 ), and various components thatfacilitate the rotation of the crankshaft within the crank frame (e.g.,the components shown in FIG. 179 ) and the coupling of crank section7122 to crosshead section 7124, drive section 7130, and base section7140. Thus, “a first means for receiving rotational motion” includescrank section 7122 and its components and the equivalents therefore. Asrecited herein, crank section 7122 (and its equivalents) may be referredto as “a first means for receiving rotational motion.” Crank section7122 and its various components are discussed herein in further detailin reference to FIGS. 179-189 .

Crosshead section 7124 is configured to couple to crank section 7122 andto translate the rotational motion into linear motion. In variousembodiments, crosshead section 7124 includes a plurality of individualcrosshead frames (e.g., crosshead frames 220 shown in FIG. 2 ) and aplurality of crosshead assemblies (e.g., crosshead assemblies 71700shown in FIG. 17 ). As recited herein, crosshead section 7124 (and itsequivalents) and its components (and their equivalents) may be referredto as “a second means for translating rotational motion into linearmotion.” Crosshead section 7124 and its various components are discussedherein in further detail in reference to FIGS. 163-179 .

Connector section 7126 is configured to couple to fluid end 100 (e.g.,by coupling to individual fluid end sections 102) such that the linearmotion is applied to fluid end 100. Connector section 7126 may includeone or more connect plates (e.g., individual connect plates 118 shown inFIG. 133 ) and one or more spacers (e.g., spacers 122 shown in FIG. 133). As recited herein, connector section 7126 (and its equivalents) andits various components (and their equivalents) may be referred to as “athird means for coupling to a fluid end 100 such that linear motion isapplied to a fluid end assembly.” Connector section 7126 and its variouscomponents are discussed herein in further detail in reference to FIGS.139-149A.

In various embodiments, the high pressure pump 101 is powered using oneor more drive sections 7130. In various embodiments, drive section 7130includes a planetary gearset, although any other suitable gearconfiguration could be used. In various embodiments shown in FIG. 132 ,drive section 7130 is powered by a diesel motor and applies rotationalmotion to crank section 7122 at one end. In other embodiments, drivesection 7130 is powered by one or more electrical motors and appliesrotational motion to crank section 7122 at one end or by a dual drivesection 7130 in which rotational motion is applied at both ends of cranksection 7122.

The power end 103 includes base section 7140 that is configured tocouple to various components of crank section 7122 and/or crossheadsection 7124. In various embodiments, by coupling crank section 7122 andcrosshead section 7124 to base section 7140, the various components ofcrank section 7122 and crosshead section 7124 are secured to one anothersuch that these components do not move relative to each other as thehigh pressure pump 101 operates. Further, base section 7140 is itselfcoupled to a truck or a trailer (not shown), such that the high pressurepump 101 may be moved to a drill site or around the drill site. Basesection 7140 is discussed in further detail here in reference to FIG.190 .

Referring now to FIGS. 133-138 , the high pressure pump 101 is shown infurther detail with drive section 7130 and base section 7140 removed.FIG. 133 is a front perspective view, FIG. 134 is a side view, FIG. 135is a rear perspective view, FIG. 136 is a rear elevational view, FIG.137 is a front elevational view, and FIG. 138 is a top view. In theembodiment shown in FIGS. 133-138 , pump 101 includes a plurality ofplates and rods that couple the crank section 7122, crosshead section7124, and connector section 7126 together.

As shown in FIG. 133 , such plates include a rear support plate 7200(also referred to herein as a crank section support plate), a centralsupport plate 7202 (also referred to herein as a center support plate),and one or more front support plates such as a top front support plate7204 and a bottom front support plate 7206. In various embodiments, rearsupport plate 7200 is coupled to a rear side of the crank section 7122,central support plate 7202 is coupled to a front side of crank section7122 and a rear side of crosshead section 7124 (and is thus disposedbetween crank section 7122 and crosshead section 7124), and top frontsupport plate 7204 and bottom front support plate 7206 are coupled tothe front of crosshead section 7124. In the embodiment shown in FIGS.132-140 , two sets of stay rods (also referred herein as sets of rods)hold high pressure pump 100 together: a first set of rods 7240 (alsoreferred to herein as crank stay rods 7240 and stay rods 7240) and asecond set of rods 120 (also referred to herein as connect plate stayrods 120 and stay rods 120), which are also discussed with regard toFIG. 6A. In the embodiment shown in FIGS. 132-140 , (a) the first set ofrods 7240 couples together top front support plate 7204 and bottom frontsupport plate 7206, crosshead section 7124, central support plate 7202,crank section 7122, and rear support plate 7200, and (b) second set ofrods 120 couples together connector section 7126, top front supportplate 7204 and bottom front support plate 7206, crosshead section 7124,and central support plate 7202. As discussed herein, in variousembodiments, fewer than two sets of stay rods may be used, more than twosets of stay rods may be used, and/or the sets of stay rods may be usedto couple the crank section 7122, crosshead section 7124, and connectorsection 7126 differently than shown in FIGS. 133-138 . Further, invarious embodiments, the various plates 7200, 7202, 7204, and 7206 mayhave different top and bottom profiles to match the shape of variousembodiments of crank section 7122 and crosshead section 7124.Additionally, various embodiments of high-pressure hydraulic fracturingpump discussed herein do not include some or all of plates 7200, 7202,7204, and 7206. Second set of rods 120 are discussed in further detailherein in reference to FIGS. 144-149A. First set of rods 7240 arediscussed in further detail herein in reference to FIGS. 150-162 . Rearsupport plate 7200 is discussed in further detail herein in reference toFIGS. 150 and 180 . Central support plate 7202 is discussed in furtherdetail herein in reference to FIGS. 150 and 164 . The one or more frontsupport plates (e.g., top front support plate 7204, bottom front supportplate 7206) are discussed in further detail herein in reference to FIGS.150 and 163 .

Crank section 7122 includes a crank frame 7210 and crankshaft 7212. Asdiscussed herein, rotational motion is applied to crankshaft 7212 (e.g.,by drive section 7130), which in turn rotates within crank frame 7210.Referring now to FIG. 136 individually, in various embodiments in whichcrank section 7122 is driven by a drive section 7130 on one side (asshown in FIG. 132 ), crank section 7122 includes a lubrication inlet7500, which is configured to attach to the crank section 7122 at theside that is opposite to drive section 7130 to facilitate lubrication ofcrankshaft 7212. In the embodiments shown in FIG. 136 , crank section7122 includes a plurality of maintenance covers 7510 secured to rearsupport plate 7200 by a plurality of fasteners 7512 (e.g., machinescrews that may be driven by a hex driver). The various components ofcrank section 7122, crank frame 7210, and crankshaft 7212 are discussedin further detail herein in reference to FIGS. 179-189 .

In various embodiments, crosshead section 7124 includes a plurality ofindividual crosshead frames 7220. In such embodiments, the individualcrosshead frames 7220 house respective crosshead assemblies (e.g.,crosshead assembly 71700 shown in FIG. 144 ) configured to translaterotational motion from crankshaft 7212 into linear motion useable todrive a plunger of a fluid end section 102 (e.g., plunger 290 shown inFIG. 139 ). The various components of crosshead section 7124 andcrosshead frames 7222 are discussed in further detail herein inreference to FIGS. 162-178 .

In various embodiments, connector section 7126 includes a plurality ofindividual connect plates 118 and a plurality of spacers 122, also shownin FIGS. 6A and 10-13 . Referring now to FIG. 134 individually, asdiscussed above, the individual connect plates 118 are configured tocouple to respective fluid end sections 102 using the fastening system146, also shown in FIG. 17 . In various embodiments, the number ofindividual connect plates 118 (and the number of crosshead frames 7220)corresponds to the number of fluid end plungers (e.g., plunger 290 shownin FIG. 20 and also discussed in reference to FIG. 139 ) which arepowered by power end 103. As discussed above, the fluid end 100 includesa plurality of individual fluid end sections 102 that each has its ownplunger 290. In such embodiments, each individual fluid end section 102has a corresponding individual connect plate 118 and crosshead frame7220 (e.g., in embodiments with five fluid end sections 102, there arefive individual connect plates 118 and crosshead frames 7220). Someembodiments of spacers 122 are discussed below in reference to FIGS.141-143 , and an alternative embodiment of spacers 122A is discussedbelow in reference to FIG. 149A. In various embodiments of power end103, either of spacers 122 or spacers 122A may be used withcorresponding modifications to connect plate 118 and plates 7204 and7206.

As shown in FIG. 134 , in various embodiments, parts of the fasteningsystem 146 are vertically offset from second set of rods 120 by verticaloffset 7302, and second set of rods 120 are vertically offset from firstset of rods 7240 by vertical offset 7304. In various embodiments,vertical offset 7302 is between 2 and 4 inches and vertical offset 7304is between 5 and 7 inches. As shown in FIG. 134 , a vertical offset 7306between the first set of rods 7240 and a longitudinal centerline A ofthe power end 103 is greater than a vertical offset 7308 between thesecond set of rods 120 and the centerline A. In various embodiments,vertical offset 7306 is between 12 and 14 inches and vertical offset7308 is between 5 and 7 inches. In embodiments such as those shown inFIGS. 132-138 , the connections coupling power end 103 together andcoupling power end 103 to fluid end 100 may be referred to collectivelyas “step down connections.” The stay rods 7240 connect the crank section7122 to the crosshead section 7124, compressing the central supportplate 7202 between them. The connect plate stay rods 120 connect thecrosshead section 7124 to the connect plates 118. Then finally theconnect plates 118 are connected to the fluid end sections 102 using thefastening system 146. As the connections get closer to the front of thepump 101, they get closer together vertically, or they “step down.” Thevertical distance between the lowest stay rod 7240 and highest stay rod7240 (i.e., vertical offset 7306 doubled) is larger than the verticaldistance between the lowest connect plate stay rod 120 and the highestconnect plate stay rod 120 (i.e., vertical offset 7308 doubled). In likemanner, the vertical distance between the lowest connect plate stay rod120 and the highest connect plate stay rod 120 is greater than thevertical distance between the lowest fastening system 146 and thehighest fastening system 146. These step downs minimize flexure in theentire assembly, allow for ease of assembly and disassembly, andgenerate a better fit between components in various embodiments.

In various embodiments, the first set of rods 7240 couples together topfront support plate 7204 and bottom front support plate 7206, crossheadsection 7124, central support plate 7202, crank section 7122, and rearsupport plate 7200 such that when the first set of rods 7240 is in astate of tension (e.g., by applying torque to the nuts 72400 shown inFIG. 150 ), the top front support plate 7204 and bottom front supportplate 7206, crosshead section 7124, central support plate 7202, cranksection 7122, and rear support plate 7200 are compressed. Similarly, invarious embodiments, the second set of rods 120 couples togetherconnector section 7126, top front support plate 7204 and bottom frontsupport plate 7206, crosshead section 7124, and central support plate7202 such that when the second set of rods 120 is in a state of tension(e.g., by applying torque to the nuts 7132 shown in FIG. 140 ) theindividual connect plates 118, spacers 122, top front support plate 7204and bottom front support plate 7206, crosshead section 7124, and centralsupport plate 7202 are compressed. Further, because first set of rods7240 extends all of the way through the top and bottom of crossheadsection 7124 and crank section 7122, the individual crosshead frames7220 and crank frame 7210 are compressed. Accordingly, these componentsin compression are preloaded above working loads (e.g., deflection andstress on the individual connect plates 118 from reciprocating plungersof fluid end 100) and from the force of gravity on the fluid end 100.

Thus, in the embodiments discussed herein in reference to FIGS. 132-190, first set of rods 7240 couples together top front support plate 7204and bottom front support plate 7206, crosshead section 7124, centralsupport plate 7202, crank section 7122, and rear support plate 7200 andsecond set of rods 120 couples together connector section 7126, topfront support plate 7204 and bottom front support plate 7206, crossheadsection 7124, and central support plate 7202. Other arrangements of stayrods may be employed in different embodiments, however, while stillincluding other aspects of the disclosure (e.g., individual connectplates 118, individual crosshead frames 7220, single-plunger fluid endsections 102, blind nuts 72408 shown in FIG. 150 , various alignmentpins and lubrication features discussed herein).

In various embodiments, the individual crosshead frames 7220 and crankframe 7210 are made (at least in part) of ductile iron, and first set ofstay rods 7240, second set of stay rods 120, rear support plate 7200,central support plate 7202, top front support plate 7204, and bottomfront support plate 7206 are made (at least in part) of high alloysteel. By using different materials in different applications, differentbeneficial properties of the different materials can be used to improvethe overall performance of power end 103. As will be understood, ductileiron (also referred to as ductile cast iron, spheroidal graphite castiron, or nodular cast iron) has improved impact and fatigue resistance,elongation, and wear resistance due to the spherical (round) graphitestructures in the metal. Further, as the individual crosshead frames7220 and crank frame 7210 are subjected to wear, the graphite embeddedin the ductile iron may act as an additional dry lubricant around thecrankshaft 7212 and crosshead assembly as they move. Additionally, thegeometry of crank frame 7210 and the individual crosshead frames 7220may be easier to manufacture with ductile iron because crank frame 7210and the individual crosshead frames 7220 can be cast from molten ductileiron, which may be easier and less expensive than machining crank frame7210 and the individual crosshead frames 7220 from blocks of high alloysteel in various instances. In contrast, high alloy steel (compared toductile iron or carbon steel) has greater properties of strength,hardness, toughness, wear resistance, corrosion resistance,hardenability, and hot hardness. Thus, a high alloy steel is better ableto accept and distribute stress from tension on first set of rods 7240and second set of rods 120, and from deflection from the reciprocatingplunger and individual connect plates 118. Further, because the rearsupport plate 7200, central support plate 7202, top front support plate7204, and bottom front support plate 7206 are plates with various boresand cutouts discussed herein, machining them from larger plates isrelatively easier and less expensive than it would be to machine crankframe 7210 and the individual crosshead frames 7220 from blocks of highalloy steel. In various embodiments, first set of rods 7240, second setof rods 120, connect plates 118, spacers 122, and/or fastening system146 may also be made (at least in part) of high alloy steel,

In various embodiments, by using two sets of rods 7240 and 120, thefunctions performed by the rods 7240 and 120 may be applied moreprecisely (i.e., compared to embodiments in which a single set of stayrods are used to couple together connector section 7126, crossheadsection 7124, and crank section 7122). In such embodiments, second setof rods 120 is configured to remove high deflection and high stress inthe connect plate 118 that might not be as effectively removed in anembodiment having a single set of stay rods because the single set ofstay rods would be spaced too far from the cylindrical axis of theplunger (i.e. centerline A shown in FIG. 134 ) to effectively eliminatethe deflection and stress if they were the only set of stay rods used.In contrast, by being closer to centerline A, second set of rods 120decreases deflection and stress on individual connect plates 118,spacers 122, and second set of rods 120 is decreased because thevertical offset 7306 is closer to centerline A. As a result, the servicelife of these components may be increased.

Referring now to FIG. 138 individually, power end 103 includes alubrication system 7700 and a plurality of fastening systems 146 thatare configured to secure fluid end 100 to connector section 7126. Invarious embodiments, lubrication system 7700 includes a lubricationdistribution manifold 7706 that is coupled to lubrication conduits 7702and connectors 7704. In various embodiments, lubrication distributionmanifold 7706 receives lubricant from a lubrication system (not shown)and distributes lubricant to crank section 7122 and crosshead section7124 via the lubrication conduits 7702 and connectors 7704. In variousembodiments, the lubrication system 7700 for the power end 103 iscoupled to a lubrication pump (not shown) to provide pressure to thelubricant to carry the pressurized lubricant to the different inputlocations on the power end 103 corresponding to the connectors 7704. Invarious embodiments discussed in further detail in reference to FIGS.144-179 , during operation lubricant is provided to inlet ports ofcrosshead section 7124 at each crosshead frame 7220 to lubricatecrosshead section 7124 (e.g., lubrication inlet bore 71900 shown in FIG.146 ) as the crosshead (e.g., crosshead assembly 71700 shown in FIG. 144) reciprocates. In various embodiments discussed in further detail inreference to FIGS. 180-189 , lubricant is provided to crank section 7122on both ends of crankshaft 7212 and at each bearing journal in crankframe 7210 (e.g., at lubrication ports 75422 shown in FIG. 180 ) toprovide lubrication to crankshaft 7212 and the corresponding portions ofcrank frame 7210. Further, in various embodiments, lubricant is allowedto flow out of crosshead section 7124 and into crank section 7122. Afterlubricating crank section 7122 and crosshead section 7124, lubricantdrains out of the bottom of crank section 7122 (e.g., through drains71908 shown in FIG. 146 ). This lubricant can be collected, filtered,supplemented as needed, and recirculated through lubrication system 7700in various embodiments.

In various embodiments, the lubrication of the power end's 103 movingcomponents is accomplished with a closed lubrication system 7700. Inthis description, a closed lubricant system is defined as the lubricantbeing separate and distinct from the fluid being pumped. A closedlubricant system is further defined to reuse the lubricant. Reuse of thelubricant involves gathering the lubricant after use, filtering it, andreusing it. Periodic addition of makeup lubricant is allowed.

Second Set of Rods 120, Connector Section 7126, and Lubrication System7700

Referring now to FIGS. 139-149A, power end 103 and components thereof(with a particular focus on second set of rods 120, connector section7126, and lubrication system 7700) are shown in further detail. FIG. 139is a front perspective view of power end 103, FIG. 140 is a frontperspective view of power end 103 with connector section 7126 exploded,FIGS. 141-143 and 147-149 are various views of components of connectorsection 7126, FIGS. 144 and 146 are cut-away side views of power end103, and FIGS. 145 and 149A are cut-away front perspective views ofpower end 103.

Referring individually to FIG. 139 , power end 103 is shown with fluidend 100 removed. With fluid end 100 removed, the plurality of plungers290 that reciprocate within fluid end 100 are easier to view. Theindividual plungers 290 are coupled to a pony rod 7804 by a pony rodclamp 7802. As discussed in further detail herein, pony rod 7804 is apart of the crosshead assembly (e.g., crosshead assembly 71700 shown inFIG. 144 ) that reciprocates as a result of the crankshaft 7212rotating. FIG. 139 also includes two vertical lines CA and CB at whichcross-sections are taken to show the internal structure of power end103. Line CA bisects two of the second set of rods 120. Line CB bisectsconnect plate 118.

Returning to FIG. 140 , a front perspective view of power end 103 with aportion of connector section 7126 exploded is shown. As can be seen fromFIG. 146 , when power end 103 is assembled, individual rods 120 of thesecond plurality of rods 120 are disposed through bores in connect plate118, as described with reference to FIGS. 10-13 and 16 . In variousembodiments, washers 134 are configured so that they eliminate the needfor a torque reaction arm when engaging the nuts 132. For example, thewashers 134 may be HYTORC™ washers. In various embodiments, the washers134 may also include a lock washer to prevent the nuts 132 from backingoff due to vibration. In various embodiments, during assembly, thewashers 134 are placed on the protruding threaded end of the rods 120,and nuts 132 are torqued to between 2500 lb.-ft. and 4000 lb.-ft. Invarious embodiments, spacers 122 are aligned to top front support plate7204 and bottom front support plate 7206 using a plurality of alignmentdowels 7906 (shown in FIG. 149 ) that are received by correspondingrecesses in spacers 122 and plates 7204 and 7206. In variousembodiments, spacers 122A are aligned to connect plate 118, top frontsupport plate 7204, and bottom front support plate 7206 using aplurality of sleeves 72220 (discussed in reference to FIG. 149A).

FIGS. 141-143 are a rear perspective view, a rear view, and a cutawayside view of an embodiment of spacer 122. As shown, spacer 122 includesa connect plate stay rod through hole 71000, a smaller diameter linearsection 71002, a conical transition section 71004, a larger diameterlinear section 71008, and a plurality of alignment dowel pin holes71006. FIGS. 141 and 142 also include a vertical line CC bisectingalignment dowel pin holes 71006. FIG. 143 is a cutaway side view of across section of spacer 122 taken at line CC.

Turning back to FIGS. 10-13 , each of the first passages 128 formed inthe connect plate 118 have counterbores 129 on the second surface 126 ofthe connect plate 118. The diameter of the counterbore 129 is the sameas the outside diameter of the smaller diameter linear section 71002 ofthe spacer 122. Using a second plurality of stay rods 120 allows thefirst passages 128 to be placed closer, vertically, to the secondpassages 142 formed in the connect plate 118 and used to attach thefluid end section 102 to the connect plate 118. This reduced distancebetween the two mounting points significantly reduces the deflection ofthe connect plate 118 during operation, particularly about thetransverse axis. While the connect plate 118 shown in FIGS. 10-13 is asubstantially flat plate, it will be understood that connect plate 118may have a concave or convex shape. Further, in some embodiments, eachof the first passages 128 may also have counterbores on the firstsurface 124 of the connect plate 118. In such embodiments, at least partof a nut 132 and washer 134 may be disposed within the counterbore.

Referring now to FIGS. 144 and 145 , FIG. 144 is a cutaway side view ofpower end 103 taken along Line CA, and FIG. 145 is a cutaway frontperspective view of power end 103 taken along Line CA, respectively. Asshown in FIGS. 144 and 145 , Line CA bisects power end 103 at the centerof two of the second set of rods 120. In the embodiments shown in FIG.144 , connect plate stay rod holes 7904 extend all of the way throughplates 7204, 7206 and crosshead frame 7220 such that the rods 120 passthrough the connect plate 118, spacers 122, connect plate stay rod holes7904 and end within threaded connect plate stay rod holes 71702 incentral support plate 7202. In various embodiments, threaded connectplate stay rod holes 71702 are female threaded recesses within centralsupport plate 7202 and are configured to receive a threaded end of a rod120. In various embodiments, the rods 120 are torqued down such that therods are “fully engaged” with threaded connect plate stay rod holes71702. As used herein, “fully engaged” means that a rod 120 has beentorqued such that the end of rod 120 inserted into the threaded connectplate stay rod hole 71702 is in contact with the base of threadedconnect plate stay rod hole 71702 (also referred to “bottoming out”). Invarious embodiments, rods 120 are fully engaged with threaded connectplate stay rod holes 71702 when the rods 120 have been torqued tobetween 2500 lb.-ft. and 4000 lb.-ft. As shown in FIG. 144 , a crossheadassembly 71700 driving pony rod 7804 is disposed within crossheadsection 7124, central support plate 7202, and crank section 7122.Crosshead assembly 71700 is discussed in further detail with referenceto FIGS. 164, 165, 177, and 178 . FIG. 144 also includes areas which invarious embodiments, includes additional features discussed in referenceto FIGS. 148 and 149 , respectively.

Referring now to FIGS. 146 and 147 , FIG. 146 is a cutaway side view ofpower end 103 taken along Line CB, and FIG. 147 is a cutaway frontperspective view of power end 103 taken along Line CB. As shown in FIGS.146 and 147 , Line CB bisects power end 103 at the center of connectplate 118. FIGS. 146 and 147 illustrate various embodiments of howlubrication system 7700 distributes lubrication within power end 103. Inthe embodiments shown in FIGS. 146 and 147 , crosshead frame 7220includes a lubrication inlet bore 71900 that is coupled to lubricationsystem 7700 to receive lubricant during operation. As crosshead assembly71700 moves within crosshead frame 7220, lubricant flows along groove72000 on the exterior of crosshead assembly 71700 and through channels71902 and 71904 within crosshead assembly 71700. In various embodiments,channel 71902 is a vertical bore that intersects with horizontal channel71904. As shown in additional detail in FIG. 178 , channel 71902 beginsbehind the front face at the top and center of the crosshead (e.g.,crosshead 73810 discussed in reference to FIG. 164 ) and continuesvertically downward until it intersects the horizontal channel 71904 atthe center of the crosshead. As shown in FIG. 146 , channel 71904 beginsat the base of the curved inner portion of the crosshead (e.g., thrustseat bearing mount 75210 discussed in reference to FIG. 178 ) on thecentral longitudinal axis of the crosshead and continues until itintersects channel 71902. Channel 71904 does not intersect the frontface of the crosshead in the embodiment shown in FIG. 146 . Lubricationis then able to pass through lubrication through bore 71920 and 71922 ofthe connecting rod of the crosshead assembly (e.g., connecting rod 73830discussed herein in reference to FIG. 165 ).

As discussed in further detail in reference to FIGS. 164, 165, 177, and178 , various components of crosshead assembly 71700 move relative toeach other such that lubricant is necessary to prevent seizing or damageto the crosshead assembly. Lubricant is able to flow from crossheadframe 7220 and through a hole in central support plate 7202 via achannel 71906 formed in crosshead frame 7220. From there, lubricant fromcrosshead section 7124 joins with lubricant flowing through crankshaftsection (discussed in reference to FIGS. 179-189 ) and flows through adrain 71908 in the base of crank frame 7210. As discussed in furtherdetail in reference to FIGS. 179-189 , crank frame 7210 includes aplurality of drains 71908, each of which is surrounded by a portion ofcrank frame 7210 that is angled towards drains 71908 to allow lubricantto drain into a sump tank (not shown) from which it is filtered andrecirculated in various embodiments. Additionally, in the embodimentsshown in FIGS. 146 and 147 , a cross-section along line CB also exposesthe alignment dowels 71910 useable to align crosshead frame 7220 withcentral support plate 7202. As shown in FIGS. 146 and 147 , alignmentdowels 71910 is received by corresponding dowel pin holes 71912 and71914 in crosshead frame 7220 and central support plate 7202,respectively.

Referring now to FIG. 148 , detail CN from FIG. 144 is shown in greaterdetail. As can be seen in FIG. 148 , spacer 122 is received incounterbore 71400 in connect plate 118, rod 120 is disposed within nut132, washer 134, connect plate 118 (e.g., by first passages 128) andspacer 122 (e.g., by connect plate stay rod through hole 71000). Asecond passage 142 used for mounting a fluid end section 102 to theconnect plate 118 is disposed above rod 120.

Referring now to FIG. 149 , an alternative embodiment of detail CO fromFIG. 144 is shown in greater detail. As can be seen in FIG. 149 , spacer122 is coupled to bottom front support plate 7206 and crosshead frame7220 by a pair of alignment dowels 7906 that are received bycorresponding alignment dowel pin holes 71006 in spacer 122 and byalignment dowel pin holes 72200 in bottom front support plate 7206 andthe lower portion of crosshead frame 7220. In various embodiments,spacers 122 are similarly coupled to top front support plate 7204 andthe upper portion of crosshead frame 7220 by alignment dowels 7906 andcorresponding alignment dowel pin holes 71006 and 72200 (not shown).

Referring now to FIG. 149A, a perspective cutaway view is shown of analternative embodiment of power end 103 taken along line CA shown inFIG. 139 . In the embodiment shown in FIG. 149A, rather than the spacer122 and alignment dowels 7906 discussed in FIGS. 148 and 149 , thisembodiment includes alternative spacers 122A and a set of sleeves 72220to facilitate alignment of spacers 122A. In this embodiment, rather thana spacer 122 with a connect plate stay rod through hole 71000, a smallerdiameter linear section 71002, a conical transition section 71004, alarger diameter linear section 71008, and a plurality of alignment dowelpin holes 71006 (shown in FIGS. 141-143 ), spacer 122A has a connectplate stay rod through hole 71000 with two larger diameter interiorsections 72210 and a single exterior diameter 72212. In the embodimentshown in FIG. 149A, the first passages 128 of connect plate 118 includesa larger diameter interior section 72222 and the connect plate stay rodholes 7904 of the plates 7204 and 7206 are slightly wider (relative tothe embodiment shown in FIG. 149 ). In the embodiment shown in FIG.149A, sleeves 72220 are disposed within larger diameter interior section72222 of connect plate 118, within larger diameter interior sections72210 of spacers 122A, and within connect plate stay rod holes 7904 tofacilitate alignment of spacer 122A with plates 7204, 7206, and connectplate 118. In such embodiments, connect plate 118 does not includecounterbore 129 and spacer 122A touches but is not received by connectplate 118.

In various embodiments, to assemble the connector section 7126 to thecentral support plate 7202, a first end of each stay rod 120 is insertedthrough connect plate stay rod holes 7904 of the plates 7204 and 7206,and connect plate stay rod holes 7904 of a crosshead frame. In variousembodiments, the stay rods 120 are torqued into the threaded holes 71702of the central support plate 7202. The spacers 122 are placed overcorresponding rods 120 and coupled to top front support plate 7204 orbottom front support plate 7206, using alignment dowels 7906 to ensureproper alignment in various embodiments. Connect plate 118 is thenplaced over spacers 122 and rods 120, using counterbores 129 to ensureproper alignment in various embodiments. Washers 134 and nuts 132 arethen placed over the protruding ends of the connect plate stay rods 120and the nuts 132 are torqued on the second end of the stay rods 120placing the connect plate stay rods 120 in tension and providing aclamping force to the components between the central support plate 7202and the nut 132 on the second end of the stay rod 120.

First Set of Rods 7240, Front Support Plates 7204, 7206, and CentralSupport Plate 7202

Referring now to FIGS. 150-164 power end 103 and components thereof(with a particular focus on first set of rods 7240) are shown in furtherdetail. FIG. 150 is a front perspective exploded view of power end 103,FIGS. 151-153 are cutaway views of portions of power end 103, and FIGS.154-161 are various views of a second nut 72408 from FIG. 150 . In thisembodiment of a high-pressure pump 101, the crank section 7122 andcrosshead section 7124 are assembled to each other using the first setof stay rods 7240, nuts 72400 and 72408, washers 72402 and 72406, asshown in FIGS. 150-153 .

Referring individually to FIG. 150 , a front perspective exploded viewof power end 103 is shown. As shown in FIG. 150 , connector section7126, second set of stay rods 120, and maintenance covers 7510 have beenremoved. FIG. 150 depicts how the first plurality of rods 7240 coupletogether the various plates 7200, 7202, 7204, and 7206; crank section7122; and crosshead section 7124 by exploding these sections relative torods 7240. In the embodiment shown in FIG. 150 , twenty rods 7240 couplerear support plate 7200 to crank section 7122, couple crank section 7122to central support plate 7202, couple central support plate 7202 tocrosshead section 7124, and couple crosshead section 7124 to top frontsupport plate 7204 and bottom front support plate 7206. Rods 7240 aresecured by nuts 72400, first washers 72402, second washers 72406, andsecond nuts 72408. As shown in FIG. 150 , rods 7240 are received bycorresponding stay rod through holes 72404 located along the top andbottom periphery of front support plate 7204, bottom front support plate7206, the individual crosshead frames 7220, central support plate 7202,crank frame 7210, and rear support plate 7200. Thus, in the depictedembodiments, to assemble crank section 7122 to crosshead section 7124,second nuts 72408 are threaded on a first end of each stay rod 7240 andthen the second end of each stay rod 7240 is inserted through a secondwasher 72406, the stay rod through holes 72404 of rear support plate7200, the stay rod through holes 72404 of crank frame 7210, the stay rodthrough holes 72404 of central support plate 7202, the stay rod throughholes 72404 of an individual crosshead frame 7220, the stay rod throughholes 72404 of either top front support plate 7204 or bottom frontsupport plate 7206, and finally first washer 72402. Once all the stayrods 7240 are inserted in the components, nuts 72400 are threaded on thesecond end of the stay rods 7240 and the specified torque (e.g., between2500 lb.-ft. and 4000 lb.-ft. in various embodiments) is applied to thenuts 72400. Once the specified torque is applied to the nuts 72400 thestay rods 7240 are in tension and provide a clamping force to thecomponents between the nuts 72400 and 72408. FIG. 150 also includes lineCD which bisects power end 103 at the center of two of rods 7240.

When assembled, top front support plate 7204 and bottom front supportplate 7206 are disposed in front of crosshead section 7124. As discussedherein, crosshead section 7124 includes a plurality of crosshead frames7220. The profiles of top front support plate 7204 and bottom frontsupport plate 7206 correspond to the profiles of the crosshead frames7220. In particular, the bottom of top front support plate 7204 includescutaways 72410 around the center bore of the crosshead frames 7220 andthe top of top front support plate 7204 includes wider portions 72412surrounding its stay rod through holes 72404. Similarly, the top ofbottom front support plate 7206 includes cutaways 72410 around thecenter bore of the crosshead frames 7220 and the bottom of bottom frontsupport plate 7206 includes wider portions 72412 surrounding its stayrod through holes 72404. In various embodiments, by having variableprofiles corresponding to the top and bottom of crosshead frames 7220,weight can be reduced from top front support plate 7204 and bottom frontsupport plate 7206 while still providing adequate surface area to absorbclamping forces from nuts 72400 and 72408. In various embodiments, topfront support plate 7204 and bottom front support plate 7206 are made ofhigh alloy steel and are between 0.490 inches and 0.530 inches thick.Further, in various embodiments, top front support plate 7204 and bottomfront support plate 7206 are separate pieces of metal rather than beinga unitary piece of metal like rear support plate 7200. By not includingmetal joining top front support plate 7204 and bottom front supportplate 7206, weight can further be reduced. Thus, top front support plate7204 and bottom front support plate 7206 are substantial enough toreduce deflection of individual components and reduce relative movementbetween components (e.g., movement between the individual crossheadframes 7220), particularly about the transverse and vertical axes,without unnecessarily increasing weight or material cost in variousembodiments.

When assembled, central support plate 7202 is disposed between crossheadsection 7124 and crank section 7122. The central support plate 7202 is agenerally rectangular plate with a plurality of stay rod through holes72404 located along the top and bottom periphery. In variousembodiments, central support plate 7202 further includes a plurality ofthe following features: lifting eye holes 72428; a variable top andbottom profile with raised portions 72430 around stay rod through holes72404; vacuum relief through bores 72432, threaded connect plate stayrod holes 71702, lubricant drain through bores 72434, dowel pin holes71914 useable for alignment with crosshead section 7124, crosshead ports72420, and dowel pin holes 72436 useable for alignment with cranksection 7122. In various embodiments, lifting eye holes 72428 areconfigured to facilitate lifting of central support plate 7202 duringassembly; vacuum relief through bores 72432 are configured to allow airfrom the individual crosshead frames 7220 to pass from crosshead frame7220 to crank section 7122; lubricant drain through bores 72434 areconfigured to allow lubricant to flow from the individual crossheadframes 7220 to crank section 7122; and dowel pin holes 72436 areconfigured to receive alignment dowel 72452 which are also received bydowel pin holes 72454 in crank frame 7210. Similarly to the variableprofile of top front support plate 7204 and bottom front support plate7206, variable profile of central support plate 7202 includes aplurality of raised portions 72430 around stay rod through holes 72404.In various embodiments, by having a variable profile, weight can bereduced from central support plate 7202 while still providing adequatesurface area to absorb clamping forces from nuts 72400 and 72408. Invarious embodiments, central support plate 7202 is made of high alloysteel and is between 2.980 inches and 3.020 inches thick. Thus, centralsupport plate 7202 is substantial enough to reduce deflection ofindividual components and reduce relative movement between components(e.g., movement between the individual crosshead frames 7220),particularly about the transverse and vertical axes, withoutunnecessarily increasing weight or material cost in various embodiments.

When assembled, rear support plate 7200 is coupled to the back of cranksection 7122. Rear support plate 7200 is a generally rectangular platewith a plurality of stay rod through holes 72404 located along the topand bottom periphery. In various embodiments, rear support plate 7200includes maintenance openings 72444, bolt holes 72442, and a variabletop and bottom profile with raised portions 72446 around stay rodthrough holes 72404. In various embodiments, bolt holes 72442 areconfigured to receive bolts (not shown in FIG. 150 ) that hold thecenter webs of rear support plate 7200 to crank frame 7210 independentlyof first set of rods 7240 and prevent rear support plate 7200 frombowing under torque load from first set of rods 7240; and maintenanceopenings 72444 are configured to be covered by maintenance covers 7510such that when a maintenance cover 7510 is removed a portion ofcrankshaft 7212 is exposed and can be serviced without removing rearsupport plate 7200. In various embodiments, by having a variableprofile, weight can be reduced from rear support plate 7200 while stillproviding adequate surface area to absorb clamping forces from nuts72400 and 72408. In various embodiments, rear support plate 7200 is madeof high alloy steel and is between 1.00 inches and 1.02 inches thick.Thus, rear support plate 7200 is substantial enough to reduce deflectionof individual components and reduce relative movement between component,particularly about the transverse and vertical axes, withoutunnecessarily increasing weight or material cost in various embodiments.

Referring now to FIGS. 151-153 , FIG. 151 is a cutaway front perspectiveview of power end 103 taken along Line CD, FIG. 152 is a cutaway sideview of power end 103 taken along Line CD, and FIG. 153 is a cutawayside view of detail CE from FIG. 152 . FIGS. 151-153 show how a pair ofrods 7240 are disposed through first washer 72402; stay rod throughholes 72404 in plates 7200, 7202, 7204, and 7206 and crosshead frame7220 and crank frame 7210; and second washer 72406 and are secured byfirst nuts 72400 and second nuts 72408. As shown in FIG. 151 , invarious embodiments, a channel 72500 is defined in crosshead frame 7220above crosshead assembly 71700. In various embodiments, channel 72500 isconfigured to allow air to flow between crank section 7122 and crossheadsection 7124 to release air that is pressurized by a forward stroke bycrosshead assembly 71700 and to relieve a vacuum that is created by aback stroke by crosshead assembly 71700. FIG. 152 includes detail CE atthe top and rear of crank section 7122 showing a cross-section of secondnut 72408. In various embodiments, including the embodiments shown inFIGS. 151-161 , second nut 72408 is a “blind nut.”

Referring now to FIGS. 154-161 , in various embodiments second nuts72408 are blind nuts. As used herein, a “blind nut” is a nut with athreaded interior and includes an opening to receive a threaded end of abolt or rod (e.g., a rod 7240) on one side of the threaded interior anda barrier on the other side of the threaded interior that prevents thethreaded end of the bolt or rod from advancing all of the way throughthe threaded interior. As discussed herein, advancing the threaded endof the bolt or rod until the bolt or rod contacts the barrier and thethreaded end of the bolt or rod cannot be further advanced, is referredto as the threaded end of the bolt or rod “bottoming out” such that thebolt or rod is “fully engaged” with the blind nut.

Referring now to FIGS. 154-161 , various views of a blind nut 72408 areshown. FIG. 154 is a side view, FIG. 155 is a rear perspective view,FIG. 156 is a rear view, FIG. 157 is a cutaway side view taken alongline CF, FIG. 158 is a front perspective view, FIG. 159 is a front view,FIG. 160 is a rear perspective view of blind nut 2408 installed on powerend 103, and FIG. 161 is a rear perspective view of detail CG from FIG.160 . As shown in FIGS. 154-161 , blind nut 72408 is a 12-point nut, butblind nut 72408 could have any number of points (e.g., 6, 8, 10, etc.).In the embodiments shown in FIGS. 154-161 , blind nut 72408 is a12-point blind nut that has a generally cylindrical shape and includesflats 72800, an internally threaded section 73100, a base 73102, aninspection bore 72900, a front face 72802, and a back face 72804. Whentorqued onto the threaded portion at the back end of the stay rod 7240,blind nut 72408 will continue to thread on the stay rod 7240 until theback end of the stay rod 7240 contacts the base 73102 of blind nut72408. In various instances, the position of the stay rod 7240 can beconfirmed visually by observation through the inspection bore 72900. Itmay also be confirmed by measurement with a depth gauge (not shown).

In various instances, the fixed position of blind nut 72408 relative tothe end of the stay rod 7240 reduces the possibility of an inadequatethreaded engagement between the two components. This positioning alsoprovides a known length of the portion of the stay rod 7240 that isinserted through the components to be assembled. Specifically, itprovides a known length of threads extending from the front side of thefront support plates 7204 and 7206. In various instances, this knownlength of thread extension gives confidence that full thread engagementwill occur between the first nut 72400 and the threaded front end of thestay rod 7240. Put another way, because the length of rods 7240 isconstant and the engagement with rods 7240 by blind nut 72408 isconstant (provided blind nut 72408 is installed fully engaged and hasnot backed off), torqueing first nuts 72400 to the designated amountwill result in a constant amount of thread on rod 7240 extending throughfirst nuts 72400. In various instances, visible inspection of thisexposed thread may be indicative of backing off by either first nut72400 and/or blind nut 72408, which may improve ease of maintenance. Ifeither first nut 72400 or blind nut 72408 are observed to be loosening,these nuts 72400, 72408 may be retorqued before causing a failure.

Thus, in various embodiments, to assemble the crank section 7122 to thecrosshead section 7124, the blind nut 72408 is torqued onto the threadedportion at the back end of a stay rod 7240 until the blind nut 72408 isfully engaged. The other, or front, end of the stay rod 7240 is theninserted through second washer 72406, the stay rod through holes 72404of plate 7200 and crank frame 7210, the stay rod through holes 72404 ofthe central support plate 7202, the stay rod through holes 72404 of thecrosshead frame 7220, the stay rod through holes 72404 of the either thetop front support plate 7204 or bottom front support plate 7206, andfirst washer 72402. A first nut 72400 is then torqued on the protrudingthreaded front end of the stay rod 7240. This process is repeated foreach of the plurality of stay rods 7240.

Crosshead Section 7124

Referring now to FIGS. 162-178 , power end 103 and components thereof(with a particular focus on crosshead section 7124) are shown in furtherdetail. FIG. 162 is a front perspective view of front support plates7204, 7206 and crosshead section 7124. FIG. 163 is a rear perspectiveview of central support plate 7202 and crosshead section 7124. FIG. 164is a front perspective exploded view of a crosshead frame 7220 (alsoreferred to as a crosshead guide) and crosshead assembly 71700. FIG. 165is a cutaway sideview of crosshead section 7124. FIGS. 166-168 arevarious views of pony rod seal housing 73800. FIGS. 169-176 are variousviews of crosshead frame 7220. FIGS. 177 and 178 are side views ofcrosshead assembly 71700.

Referring individually to FIG. 162 , the fronts of crosshead section7124, top front support plate 7204, and bottom front support plate 7206are shown. As shown in FIG. 162 , crosshead assembly 71700 has beenremoved. As can be seen in FIG. 162 , the top profile of top frontsupport plate 7204 corresponds with the top profile of the plurality ofcrosshead frames 7220 and the cutaways 72410 of the top front supportplate 7204 corresponds to the central opening of the plurality ofcrosshead frames 7220. Similarly, the bottom profile of bottom frontsupport plate 7206 corresponds with the bottom profile of the pluralityof crosshead frames 7220 and the cutaways 72410 of the bottom frontsupport plate 7206 correspond to the central opening of the plurality ofcrosshead frames 7220 and the recess disposed beneath each centralopening (e.g., base section attachment clearance 74400 discussed inreference to FIGS. 169-176 ).

Referring now to FIG. 163 , the backs of crosshead section 7124 andcentral support plate 7202 are shown. As shown in FIG. 163 , the top andbottom profile of central support plate 7202 corresponds with the topand bottom profile of the plurality of crosshead frames 7220. Asdiscussed elsewhere herein, various holes in central support plate 7202correspond with holes in the plurality of crosshead frames 7220 (e.g.,stay rod through holes 72404; vacuum relief through bores 72432,threaded connect plate stay rod holes 71702, lubricant drain throughbores 72434, dowel pin holes 71914, crosshead ports 72420, and dowel pinholes 72436). In the embodiment shown in FIG. 163 , central supportplate 7202 also includes a lower dowel hole 73700, a threaded jack bolthole 73702, and a mounting hole 73704. In such embodiments, dowel hole73700 is configured to receive an alignment dowel 71910 to facilitatealignment with crosshead frames 7220, threaded jack bolt hole 73702 isconfigured to receive a jack bolt to facilitate disengagement of centralsupport plate 7202 and crosshead frames 7220, and mounting hole 73704 isconfigured to receive a fastener to mount the central support plate 7202to the crank frame 7210.

Referring now to FIGS. 164 and 165 , a front perspective exploded viewand a cutaway side view along line CB (shown in FIG. 139 ) of acrosshead frame 7220 and a crosshead assembly 71700 are shown,respectively. As shown in FIG. 164 , various components of crossheadassembly 71700 are individually shown from pony rod 7804 to the portionsof crosshead assembly 71700 that are coupled to crankshaft 7212.Crosshead assembly 71700 includes pony rod clamp 7802, pony rod sealhousing 73800, pony rod 7804, crosshead 73810, connecting rod 73830 andvarious fasteners and bearings. As used herein, crosshead assembly 71700includes pony rod 7804 and pony rod clamp 7802, but does not includeplunger 290. As shown in FIG. 164 , portions of crosshead assembly 71700(e.g., pony rod 7804 and crosshead 73810) reciprocate within the centralbore of crosshead frame 7220 (e.g., central bore 74600 discussed inreference to FIGS. 169-176 ). The internal structure of crossheadassembly 71700 is discussed in further detail herein in reference toFIG. 178 .

As discussed herein, pony rod 7804 is coupled to plunger 290 by pony rodclamp 7802. In various embodiments, pony rod clamp 7802 is a ring-shapedclamp that is configured to couple plunger 290 to pony rod 7804. Invarious embodiments, pony rod clamp 7802 is configured to couple toplunger 290 and pony rod 7804 by receiving a flange 73803 of plunger 290and a flange 73804 of pony rod 7804. In various embodiments, the flanges73803 and 73804 are retained using a set of bolts 73806 that aredisposed in corresponding holes in pony rod clamp 7802.

As shown in FIG. 164 , pony rod seal housing 73800 is secured tocrosshead frame 7220 by inserting a set of fasteners 73802 through ponyrod seal housing 73800 and into corresponding holes in crosshead frame7220 (e.g., threaded holes 74500 shown in FIG. 171 ). In variousembodiments, pony rod 7804 is coupled to crosshead 73810 by fasteners73820 that are disposed through a mounting flange 73821 of pony rod 7804and into corresponding bores 73811 of crosshead 73810. In variousembodiments, a pony rod seal 73801 is a ring-shaped radial seal that isreceived by pony rod seal housing 73800 and secured within pony rod sealhousing 73800 by fasteners 73808 that are disposed within correspondingholes in pony rod seal housing 73800. In various embodiments, washers73809 are disposed between fasteners 73808 and pony rod seal housing73800. In various embodiments, pony rod seal 73801 seals against ponyrod 7804 as it reciprocates (e.g., sealing lubricant from crossheadframe 7220 from flowing out of the front of the central bore ofcrosshead frame 7220, preventing liquids, dust, sand, etc. from enteringthe central bore of crosshead frame 7220).

Crosshead 73810 as shown in FIGS. 164, 165, 177 and 178 , is a generallycylindrical prism. In various embodiments, crosshead 73810 includes ablind bore on the longitudinal axis that begins at the back face of thecrosshead 73810. The bore may be to a depth of up to half the length ofthe crosshead 73810 and the diameter may be large enough to leave arelatively thin wall. In various embodiments, crosshead 73810 includes apair of main bearing clearance cut outs 73813. In various embodiments,the main bearing clearance cut outs 73813 have a generally rectangularshape as viewed from either side. In various embodiments, crosshead73810 includes a wrist pin bore 73812. In such embodiments, wrist pinbore 73812 is a through bore with a transverse axis and is approximatelylongitudinally centered on the crosshead 73810. In various embodiments,wrist pin 73814 is disposed inside wrist pin bore 73812 and secured witha bracket 73816 and fasteners 73818 disposed through bracket 73816 andinto corresponding bores set in a counterbore around wrist pin bore73812. Thrust seat bearing 73822 is disposed within crosshead 73810(e.g., on a thrust seat bearing mount 75210 shown in FIG. 178 ) andsecured by thrust seat bearing keepers 73824 and fasteners 73826extending through thrust seat bearing keepers 73824 and intocorresponding bores in crosshead 73810. As discussed herein in referenceto FIG. 147 , a set of grooves 72000 are formed in the outer cylindricalsurface of the crosshead 73810 in various embodiments. In suchembodiments, grooves 72000 include two circumferential grooves connectedby a longitudinal groove 72000, as shown in FIG. 164 . In variousembodiments, neither the two circumferential grooves 72000 nor thelongitudinal groove 72000 intersect the front or the back face of thecrosshead 73810.

In various embodiments, thrust seat bearing 73822 has the general formof a thin walled hollow semi-cylinder and includes a through hole 73823and a plurality of axial grooves and a partial circumferential groovelocated on the inner surface (not shown). In various embodiments, theseaxial grooves are formed at an angle to the longitudinal axis of thethrust seat bearing 73822 but generally extend from just inside one endwall to just inside the opposite end wall and do not intersect the endwalls. In various embodiments, the partial circumferential groove iscentered longitudinally and intersects every axial groove. In variousembodiments, through hole 73823 is disposed in the center of thecircumferential groove.

In various embodiments, thrust seat bearing keeper 73824 is generallyshaped like a rectangular prism with the upper corners at each end ofits longitudinal face removed. In various embodiments, the thrust seatbearing keeper 73824 includes two through slots and two through holesoriginating on the front face, each of which is configured to receive afastener 73826. In various embodiments, the two holes are spacedequidistant from the longitudinal center and centered vertically, andthe two slots are also spaced equidistant from the longitudinal centerbut are spaced farther apart than the holes and centered vertically.

In various embodiments, a wrist pin bushing 73834 is disposed aroundwrist pin 73814. In various embodiments, wrist pin bushing 73834 is athin walled cylinder that is configured to be coupled to connecting rod73830 such that connecting rod 73830 and wrist pin bushing 73834 areable to rotate around wrist pin 73814 as crosshead assembly 71700operates.

In various embodiments, connecting rod 73830 generally appears as afirst cylinder having a shorter second cylinder formed on one end and ashorter semi-cylinder formed on the opposite end. The longitudinal axesof the second cylinder and the semi-cylinder are parallel to each otherand transverse to the longitudinal axis of the first cylinder. Invarious embodiments, connecting rod 73830 includes: a first endproximate to the wrist pin and a second end proximate to the crankshaft7212, a wrist pin bore 73835, and a lubrication through bore 71920. Thefirst end includes a curved exterior thrust seat that faces the front ofpower end 103. The wrist pin bore 73835 is a through bore through thecenter of the first end. The wrist pin bore 73835 axis is transverse tothe connecting rod 73830 longitudinal axis. The lubrication conduit71920 has a longitudinal axis and is centered transversely on the thrustseat. The lubrication through bore 71920 begins at the thrust seat andcontinues into the wrist pin bore 73835. The lubrication through bore71920 is aligned with a lubrication through bore in the second end(e.g., lubrication through bore 71922 shown in FIGS. 146 and 165 ). Atthe second end, connecting rod 73830 includes a crankshaft bearing mountsurface 73832. In various embodiments, the crankshaft bearing mountsurface 73832 is semi-cylindrical with an axis transverse to thelongitudinal axis of the connecting rod and parallel to the wrist pinbore 73835 axis. In various embodiments, connecting rod 73830 is aunitary body that is more than 24.5 inches long center-to-center (e.g.,from wrist pin bore 73835 to the center of crankshaft bearing mountsurface 73832). In some embodiments, connecting rod 73830 is 26.75inches long center-to-center. In various embodiments, connecting rod73830 is more than three times longer than the stroke of the power endassembly (i.e., the amount of movement of plunger 290 between thefurthest extent of a forward stroke of crosshead assembly 71700 and thefurthest extent of a back stroke of crosshead assembly 71700).

In various embodiments, connecting rod 73830 is coupled to crankshaft7212 using a two-piece connecting rod bearing that includes a connectingrod bearing (rod side) 73838 and connecting rod bearing (cap side)73842. In such embodiments, the two-piece connecting rod bearing issecured to connecting rod 73830 by a connecting rod cap 73844 that issecured using a plurality of fasteners 73846 that are disposed throughconnecting rod cap 73844 and into corresponding bores in the walls ofcrankshaft bearing mount surface 73832. In various embodiments,alignment pins 73836 are also received by connecting rod 73830 andconnecting rod cap 73844 to aid alignment. In various embodiments,connecting rod bearing (cap side) 73842 and connecting rod bearing (rodside) 73838 have a general shape of a hollow semi-cylinder. In variousembodiments, connecting rod bearing (rod side) 73838 includes alubricant through hole (not shown) that, when installed, is aligned withthe lubrication through bore 71922 of connecting rod 73830.

Referring now individually to FIG. 165 , a cutaway side view along lineCB (shown in FIG. 139 ) of crosshead frame 7220 and part of crossheadassembly 71700 is shown. In particular, FIG. 165 shows a spatialrelationship between various embodiments of pony rod 7804 and otherportions of crosshead assembly 71700, pony rod seal 73801, pony rod sealhousing 73800, and crosshead frame 7220. As shown in FIG. 165 , pony rod7804 is disposed through pony rod seal 73801 and pony rod seal housing73800 such that pony rod seal 73801 seals against pony rod 7804. Invarious embodiments, pony rod seal housing 73800 is disposed on a frontface of the crosshead frame 7220 and includes a circumferential groovethat receives a seal 73902 that seals the outer circumference of ponyrod seal housing 73800 against the wall that defines the central bore ofcrosshead frame 7220. In various embodiments, pony rod seal housing73800 includes a recess 73900 configured to provide additional clearancefor pony rod clamp 7802 as it reciprocates within connector section7126. Further, FIG. 165 illustrates as a dotted line 73910 path in whichlubrication is able to flow through crosshead assembly 71700 in thevarious conduits discussed herein.

Referring now to FIGS. 166-168 , a cutaway side view, a frontperspective view, and a front view of pony rod seal housing 73800 areshown, respectively. In various embodiments, pony rod seal housing 73800is a generally flat plate with a generally octagonal shape. In theembodiments shown in FIGS. 166-168 , pony rod seal housing 73800includes recess 73900, a central through hole 74000, a seal groove74002, a plurality of through holes 74100, and a plurality of throughholes 74102. In various embodiments, seal groove 74002 is acircumferential groove in the wall of the central through hole 74000 andis configured to receive at least a portion of pony rod seal 73801. Invarious embodiments, the plurality of through holes 74100 havelongitudinal axes and may be spaced around the circumference of the ponyrod seal housing 73800. In various embodiments, through holes 74100receive fasteners 73802 to couple pony rod seal housing 73800 tocrosshead frame 7220. In various embodiments, the plurality of throughholes 74102 are positioned around central through hole 74000 and areconfigured to receive fasteners 73808 to secure pony rod seal 73801within seal groove 74002.

Referring now to FIGS. 169-176 , various views of an embodiment ofindividual crosshead frame 7220 are shown: FIG. 169 is a cutawaysideview along line CI; FIG. 170 is a front perspective view; FIG. 171is a front view; FIG. 172 is a cutaway sideview along line CJ; FIG. 173is a cutaway front view along line CK; FIG. 174 is a rear perspectiveview; FIG. 175 is a rear view, and FIG. 176 is a cutaway side view alongline CL In the embodiment shown in FIGS. 169-176 , the individualcrosshead frames 7220 are generally rectangular prisms defining aplurality of bores including connect plate stay rod holes 7904, stay rodthrough holes 72404, a central bore 74600, a plurality of weightreducing cut out sections 74300, a center web support 74602, a basesection attachment clearance 74400, and various other bores configuredto receive alignment dowels, fasteners, or permit the flow of air orlubricant as discussed herein. As discussed herein, in variousembodiments, crosshead frame 7220 is made of cast ductile iron.

In various embodiments, central bore 74600 is centered on the front faceof crosshead frame 7220 and is a through bore configured to receive aportion of crosshead assembly 71700 (e.g., pony rod 7804, crosshead73810, etc.). As shown in FIGS. 169-176 , central bore 74600 is muchlarger than the various other bores in crosshead frame 7220. In variousembodiments, the walls of crosshead frame that defines the central bore74600 maintain at least a minimum thickness (e.g., at least 0.5 inchesthick) throughout but also define various weight reduction features suchas weight reducing cut out sections 74300.

In various embodiments, each individual crosshead frame 7220 definesfour connect plate stay rod holes 7904 and four stay rod through holes72404. In various embodiments, connect plate stay rod holes 7904 andstay rod through holes 72404 are smooth bores through crosshead frame7220. As discussed herein, in various embodiments, connect plate stayrod holes 7904 are located near the center of crosshead frame 7220 andstay rod through holes 72404 are located close to the top and bottom ofcrosshead frame 7220 as shown in FIGS. 169-176 . In various embodiments,the walls of crosshead frame that defines the connect plate stay rodholes 7904 and stay rod through holes 72404 maintain at least a minimumthickness (e.g., at least 0.5 inches thick) throughout but also definevarious weight reduction features. Such weight reduction featuresinclude weight reducing cut out sections 74300, base section attachmentclearance 74400, and/or the variable top and bottom profile of crossheadframe 7220 in various embodiments. In various embodiments, the walls ofcrosshead frame 7220 that define connect plate stay rod holes 7904 andstay rod through holes 72404 are thicker at the front of crosshead frame7220 than at the back of crosshead frame 7220 to transfer compressionfrom first nuts 72400 and nuts 132. For example, the walls of crossheadframe 7220 around connect plate stay rod holes 7904 at the top andbottom of crosshead frame 7220 define ribs that include a thickerportion 74422, a thinner portion 74426, and a transition portion 74424in between. In various embodiments, for example, the walls of thickerportion 74422 are twice as thick as the walls of thinner portion 74426.Between the ribs defining connect plate stay rod holes 7204 is arecessed portion 74428, and on the sides of the walls defining connectplate stay rod holes 7204 are corners 74430. In contrast to a crossheadframe in which all of the top and bottom of crosshead frame is as thickas thicker portion 74422, by defining thinner portion 74426, transitionportion 74424, recessed portion 74428, and corners 74430 material can beomitted from crosshead frame 7220, thereby reducing its weight invarious embodiments. Further, because in various embodiments crossheadframe 7220 is cast, these features also reduce the material cost of thecrosshead frame 7220.

In various embodiments, crosshead frame 7220 includes a plurality ofweight reducing cut out sections 74300 in the sides of crosshead frame7220. In various embodiments, there is a weight reducing cut out section74300 on either side of crosshead frame 7220. As discussed herein, thewalls of crosshead frame 7220 maintain a minimum thickness aroundcentral bore 74600, connect plate stay rod holes 7904, and stay rodthrough holes 72404. In various embodiments, weight reducing cut outsection 74300 are shaped such that this minimum thickness is maintainedwhile weight is removed. Further, because in various embodimentscrosshead frame 7220 is cast, weight reducing cut out section 74300 alsoreduces the material cost of the crosshead frame 7220. As shown in FIGS.170, 173, and 174 the front and rear faces of crosshead frame 7220 arethicker than interior portions in various embodiments. In suchembodiments, by having the front and rear faces be relatively thicker,compression on crosshead frame 7220 can be absorbed at the faces beingcompressed and distributed throughout the interior portions of crossheadframe. In various embodiments (and as shown in FIG. 173 ), the weightreducing cut out sections 74300 do not extend from one side of crossheadframe 7220 to the other, and have a center web support 74602 betweenthem at the top and the walls of crosshead frame 7220 defining channel71906 between them at the bottom.

Referring to FIGS. 170-172 , in various embodiments, crosshead frame7220 includes a base section attachment clearance 74400. In variousembodiments, base section attachment clearance 74400 is a generallytriangular-shaped recess with a blunted interior corner. In variousembodiments, a base section attachment hole 74402 is defined in thebottom of base section attachment clearance 74400 and is configured toreceive a fastener (e.g., a stud 76402 and a nut 76404 shown in FIG. 190) that secures crosshead frame 7220 to base section 7140. In variousembodiments, base section attachment clearance 74400 is shaped to enablesufficient room for a tool (e.g., a wrench) to access a fastenerdisposed in base section attachment hole 74402 such that crosshead frame7220 may be removed from base section 7140 or installed on base section7140. In various embodiments, base section attachment clearance 74400also serves to further reduce the weight of crosshead frame 7220. Invarious embodiments, the top corners 74420 of base section attachmentclearance 74400 extend toward the interior of crosshead frame 7220 toensure the minimum thickness of connect plate stay rod holes 7904.

Referring to FIGS. 174-176 , in various embodiments, crosshead frame7220 includes a seal 74800 around the various holes and bores discussedherein (other than holes 72404). Seal 74800 engages with central supportplate 7202 to help prevent lubrication from leaking out of crossheadframe 7220 at the joint with central support plate 7202. In variousembodiments, seal 74800 is an extruded and spliced seal that ispositioned in a groove formed in the rear side of crosshead frame 7220.In various embodiments, by using a seal 74800 instead of a gasket,various drawbacks associated with gaskets (e.g., saturation, overcompression) may be avoided. In various embodiments, crosshead frame7220 also includes seals 74802 around connect plate stay rod holes 7904.The seals 74802 engage with central support plate 7202 to preventlubrication from entering connect plate stay rod holes 7904 and leakingout of crosshead frame 7220.

In various embodiments, the front face of crosshead frame 7220 includesa plurality of threaded holes 74500 disposed around central bore 74600.As discussed herein, in various embodiments, threaded holes 74500receive fasteners 73802, thereby securing pony rod seal housing 73800 tothe front of central bore 74600. In various embodiments, the top ofcrosshead frame 7220 includes at least two holes: lubrication inlet bore71900 that is coupled to lubrication conduit 7702 to receive lubricantduring operation as discussed herein, and a lifting eye bore 74410 whichis configured to facilitate lifting of crosshead frame 7220 duringassembly. In various embodiments, lubrication inlet bore 71900 ispartially threaded at the top. The threaded portion begins at the topsurface and may extend to half of the bore depth. The threaded portionis configured to receive connector 7704 from the lubrication system7700. In various embodiments, a conduit may be disposed withinlubrication inlet bore 71900 to facilitate lubrication. In addition tolubrication inlet bore 71900, crosshead frame 7220 also defines channel71906 configured to allow lubrication to flow into crank section 7122and channel 72500 that allows air to flow between crank section 7122 andcrosshead section 7124 to release air that is pressurized by a forwardstroke by crosshead assembly 71700 and to relieve a vacuum that iscreated by a back stroke by crosshead assembly 71700. In variousembodiments, channel 71906 and channel 72500 open to central bore 74600and the rear face of crosshead frame 7220, but neither of channel 71906nor channel 72500 open to the front face of crosshead frame 7220.

In various embodiments, employing individual crosshead frames 7220allows for further weight reduction relative to a unitary crossheadsection. For example, if two crosshead frames 7220 are arrangedside-by-side, weight reducing cut out sections 74300 of the adjacentsides of the crosshead frames 7220 result in at least some of the areabetween the central bores 74600 of the crosshead frames 7220 to benegative space rather than solid material that would connect a unitarycrosshead section. Additionally, using individual crosshead frames 7220means that if a single crosshead frame 7220 in a crosshead section 7124fails (e.g., because crosshead 73810 has eroded central bore 74600 ofthe crosshead frame 7220), the failed crosshead frame 7220 may beindividually replaced rather than replacing the entire crosshead section7124. Replacement may be further aided by the various alignment pinsdiscussed herein helping to align the replacement with the rest of powerend assembly 7120. Further, because replacing an individual crossheadframe 7220 with a new crosshead frame 7220 will take less time thanrepairing a damaged crosshead frame, power end 103 may be brought backinto service faster relative to repairing a unitary crosshead section.In various instances, it is also easier and/or less costly to cast asmaller piece such as an individual crosshead frame 7220 rather than aunitary crosshead section. In various embodiments, constructing acrosshead section 7124 using a plurality of individual crosshead frames7220 may result in weight reduction, cost savings, less down time, andvarious other improvements relative to a unitary crosshead section.

Referring now to FIGS. 177 and 178 , a sideview and cutaway sideview ofplunger 290 and crosshead assembly 71700 are shown respectively. FIGS.177 and 178 show how various components shown in FIGS. 164 and 165interface with each other when crosshead assembly 71700 is assembled. Asshown, the spatial relationship between a narrow portion 75110 ofconnecting rod 73830[[,]] and a wider portion of connecting rod 73830results in clearance 75100 between connecting rod 73830 and crosshead73810. In various embodiments, by reducing weight in the sides ofcrosshead 73810 (e.g., with main bearing clearance cut outs 73813),overall weight of crosshead 73810 can be reduced without reducing theamount of material on the top and bottom of crosshead 73810. In variousembodiments, because the top and bottom of crosshead 73810 contact thewalls of crosshead frame 7220 that define central bore 74600 ascrosshead assembly 71700 reciprocates, it is on the top and bottom ofcrosshead 73810 and the corresponding portions of crosshead frame 7220that experience the most wear. Further, clearance 75100 allows more roomsuch that connecting rod 73820 can be longer. Compared to crossheadsused in other types of power ends, crosshead 73810 is both longer andhas a wider diameter. Additionally, as discussed herein, connecting rod73830 is longer than connecting rods in other power ends. As a result,pressure-velocity loading on the linear portions of crosshead assembly71700 and crosshead frame 7220 can be reduced. Further, main bearingclearance cut outs 73813 also provides clearance around crankshaft 7212when crosshead assembly 71700 is backstroking. Additionally, in variousembodiments, connecting rod 73830 is made of a single piece, which mayreduce manufacturing and labor costs compared to a connecting rod madeof multiple pieces.

Referring now to FIG. 178 , a cutaway sideview of plunger 290 andcrosshead assembly 71700 is shown. As shown in FIG. 178 , connecting rodcap 73844 is coupled to the back of connecting rod 73830, trapping aconnecting rod bearing (rod side) 73838 and connecting rod bearing (capside) 73842, which are wrapped around crankshaft 7212 (not shown in FIG.178 ). In various embodiments, connecting rod cap 73844 includes athreaded hole 75200 configured to facilitate separating connecting rodcap 73844 from crosshead assembly 71700. As shown in FIG. 178 , aninterior surface of crosshead 73810 defines a thrust seat bearing mount75210 that receives thrust seat bearing 73822 and fasteners 73826 andare attached to the interior of crosshead 73810. In various embodiments,both plunger 290 and pony rod 7804 are hollow. In the embodiment shownin FIG. 178 , pony rod 7804 includes a thinner-walled portion 75220proximate to crosshead 73810 and a thicker walled portion 75222proximate to plunger 290. Similarly, plunger 290 includes athinner-walled portion 75230 proximate to fluid end section 102 and athicker-walled portion 75232 proximate to pony rod 7804. In otherembodiments, however, either or both of plunger 290 and pony rod 7804may be solid (i.e., the hollow areas defined by thinner-walled portion75220 and thicker walled portion 75222 in pony rod 7804 andthinner-walled portion 75230 and thicker-walled portion 75232 of plunger290 are not present). FIG. 178 also includes dotted line 73910 thatillustrates the path that lubrication is able to flow through crossheadassembly 71700 in the various conduits discussed herein. As shown inFIG. 178 , lubrication is able to flow from crosshead 73810 toconnecting rod 73830 and then to lubricate connecting rod bearing (rodside) 73838 and connecting rod bearing (cap side) 73842.

Crank Section 7122

Referring now to FIGS. 179-189 , power end 103 and components thereof(with a particular focus on crank section 7122) are shown in furtherdetail. FIG. 179 is a front perspective exploded view of crank section7122 and rear support plate 7200. FIG. 180 is a rear perspective view ofcrank section 7122, rear support plate 7200, and first set of rods 7240.FIG. 181 is a cutaway side view of crank section 7122. FIG. 182 is aperspective rear view of crank frame 7210. FIG. 183 is a side view ofthe crank frame 7210. FIG. 184 is a bottom view of crank frame 7210.FIG. 185 is a perspective bottom view of crank frame 7210. FIG. 186 is afront view of crank frame 7210. FIG. 187 is a perspective view of anembodiment of crankshaft 7212. FIG. 188 is a perspective view of anotherembodiment of crankshaft 7212. FIG. 189 is side view of crankshaft 7212with dashed lines showing various internal structures of crankshaft7212.

Referring now to FIG. 179 , various components of crank section 7122 andrear support plate 7200 are shown separately in exploded form. As shownin FIG. 179 , crank section 7122 includes crank frame 7210 and acrankshaft 7212 made of various subcomponents and coupled to crank frame7210 by brackets and fasteners. In the embodiment shown in FIG. 178 ,rear support plate 7200 is configured to couple to the back of cranksection 7122 (e.g., using first plurality of rods 7240) and in turn hasa plurality of components coupled to its back.

In the embodiment shown in FIG. 179 , crank section 7122 includes crankframe 7210, a plurality of main bearings 75300, a plurality of sets ofbrackets 75350 and fasteners 75352, and crankshaft 7212. In variousembodiments, main bearings 75300 include an inner race, a roller cage,and an outer race. In various embodiments, the outer race includes oneor more radial holes to allow lubricant access to the inner race androller cage. In various embodiments, the outer race includes one or moregrooves that act as reservoirs for lubricant. In the embodiment shown inFIG. 179 , an endplate 75320 is attached to crank frame 7210 by aplurality of fasteners 75322. In various embodiments, endplate 75320covers the exterior facing side of the outer main bearings 75300. Thisreduces contamination in the main bearings 75300 and also keepslubricant contained in the crank frame 7210 so that it may exit throughthe drains 71908 instead of leaking out of the crank frame 7210requiring replacement lubricant be added to the power end lubricationsystem 7700. As shown in FIG. 179 , a lubrication inlet 7500 includes aninterior portion 75318 that is received by a hole through endplate75320. In various embodiments, lubrication inlet 7500 is stationary ascrankshaft 7212 rotates while interior portion 75318 rotates withcrankshaft 7212. In the embodiment shown in FIG. 179 , on the oppositeside of crank frame 7210 from endplate 75320, a connecting adapter 75308is coupled to crankshaft 7212 by a plurality of fasteners 75310. One ormore locating pins 75306 is configured to aid in the alignment ofconnecting adapter 75308, a fixed bearing retention ring 75312 isdisposed around a fixed center main bearing 75300 that preventstransverse crankshaft 7212 movement, and a gearbox adapter flange 75316coupled to crank frame 7210. In various embodiments, a plurality offasteners 75314 and a plurality of studs 75315 are received bycorresponding holes formed in the side of crank frame 7210 (holes 75700and 75702, respectively shown in FIG. 183 ) and corresponding holes ingearbox adapter flange 75316 to secure gearbox adapter flange 75316 tocrank frame 7210 and to prevent failures in crank frame 7210 (e.g., dueto misalignment), respectively. In various embodiments, gearbox adapterflange 75316 and connecting adapter 75308 are configured to attach todrive section 7130 such that drive section 7130 turns connecting adapter75308 to cause crankshaft 7212 to rotate within crank frame 210 on mainbearings 75300.

In various embodiments, crank frame 7210 is a unitary body that receivescrankshaft 7212 and facilitates the operation of crankshaft 7212 withincrank frame 7210. In various embodiments, crank frame 7210 is roughlyshaped as a rectangular prism with flat front and rear surfaces thatcouple to plates 7202 and 7200, respectively, and roughly square leftand right surfaces with protruding flat circular surfaces that couple todrive section 7130 on one or both sides. As discussed herein, crankframe 7210 defines main bearing bore 75340 and receives crankshaft 7212and main bearings 75300. In various embodiments, crank frame 7210protects crankshaft 7212 by preventing damage to the various movingparts of crankshaft 7212 and facilitates the operations of crankshaft7212. In various embodiments, main bearings 75300 may be secured withina plurality of bearing support walls 75356 that are evenly spacedtransversely across the crank frame 7210. Each bearing support wall75356 defines a main bearing bore 75340 and includes a plurality ofthrough holes 75354. In various embodiments, main bearing bore 75340 iscentered in the bearing support walls 75356 and bored transverselythrough them, and through holes 75354 are located around the edge of themain bearing bore 75340. In various embodiments, a main bearing 75300 isdisposed within main bearing bore 75340 at each bearing support walls75356. The main bearings 75300 are secured by sets of brackets 75350 andfasteners 75352. In various embodiments, sets of four brackets 75350secure the main bearings 75300 at both ends of crank frame 7210 and setseight brackets 75350 secure the main bearings 75300 between the twoends. In various embodiments, main bearings are secured by the brackets75350 trapping the main bearings 75300 within main bearing bore 75340and are secured by fasteners 75352 that are received by correspondingholes through brackets 75350 and holes 75354.

In various embodiments, crank frame 7210 includes a plurality ofconnecting rod cut outs 75342 between the bearing support walls 75356through which crosshead assembly 71700 (not shown in FIG. 179 )reciprocates. In various embodiments, a plurality of seals 75344 aredisposed around connecting rod cut outs 75342 (e.g., to preventlubricant from leaking out of power end 103, to prevent contaminantsfrom entering power end 103). In some of such embodiments, seals 75344are extruded and spliced seals and are positioned in grooves around eachconnecting rod cut out 75342. In various embodiments, by using a seal75344 instead of a gasket, various drawbacks associated with gaskets(e.g., saturation, over compression) may be avoided. In variousembodiments, the front of crank frame 7210 includes one or more dowelpin holes 72454 useable to facilitate alignment of central support plate7202 and the various crosshead frames 7220 as discussed herein.

In various embodiments, rear support plate 7200 is coupled to the backof crank section 7122. The rear support plate 7200 is a generallyrectangular plate with a plurality of stay rod through holes 72404located along the top and bottom periphery. In various embodiments, rearsupport plate 7200 includes maintenance openings 72444, holes 72442, anda variable top and bottom profile with raised portions 72446 around stayrod through holes 72404. In various embodiments, holes 72442 areconfigured to receive fasteners 75336 to facilitate covering ofmaintenance openings 72444 by maintenance covers 7510 such that when amaintenance cover 7510 is removed a portion of crankshaft 7212 isexposed and can be serviced without removing rear support plate 7200. Insome embodiments, a maintenance cover gasket 75330 is coupled to rearsupport plate 7200 by fasteners 75336 and maintenance cover 7510 is inturn coupled to maintenance cover gasket 75330 by fasteners 7512. Insuch embodiments, maintenance cover gasket 75330 includes a molded sealon a metal sheet backing and is configured to seal the joint betweenrear support plate 7200 and maintenance covers 7510. In suchembodiments, therefore, common drawbacks with other types of gaskets(e.g., saturation, over compression) may be avoided. In otherembodiments, no maintenance cover gasket 75330 is present andmaintenance cover 7510 is coupled directly to rear support plate 7200(e.g., by fasteners 7512). In some of such embodiments, grooves are cutaround maintenance openings 72444 and a seal is positioned in thegrooves to seal against maintenance covers 7510.

Maintenance covers 7510 are generally flat plates with a plurality ofholes around the periphery to access fasteners 7512. In variousembodiments, there is one maintenance cover 7510 (and in someembodiments, one maintenance cover gasket 75330) for each maintenanceopening 72444.

Referring now to FIGS. 180-186 , various views of an embodiment of crankframe 7210 are shown. FIG. 180 is a rear perspective view of crank frame7210, rear support plate 7200, and first set of rods 7240. FIG. 181 is acutaway sideview of crank section 7122. FIG. 182 is a perspective rearview of crank frame 7210. FIG. 183 is a side view of crank frame 7210.FIG. 7184 is a bottom view of crank frame 7210. FIG. 185 is aperspective bottom view of crank frame 7210. FIG. 186 is a front view ofcrank frame 7210. In various embodiments, crank frame 7210 is agenerally hollow rectangular prism with the long sides perpendicular tothe defined longitudinal axis and a plurality of evenly spaced bearingsupport walls 75356. As discussed herein, crank frame 7210 and rearsupport plate 7200 include a plurality of stay rod through holes 72404located along the top and bottom periphery that are configured toreceive rods 7240. In various embodiments, crank frame 7210 includes aplurality of feet 75400 at various positions around the base of crankframe 7210, a plurality of lubrication ports 75422, and/or a pluralityof weight-reduction recesses discussed herein.

Referring now to FIGS. 180 and 182-186 , in various embodiments, crankframe 7210 defines twenty stay rod through holes 72404 and variousweight reducing features. In various embodiments, stay rod through holes72404 are smooth bores through crank frame 7210. As discussed herein, invarious embodiments, stay rod through holes 72404 are located close tothe top and bottom of crank frame 7210. In various embodiments, thewalls of crank frame 7210 that defines the stay rod through holes 72404maintain at least a minimum thickness (e.g., at least 0.750 inchesthick) throughout but also define various weight reduction features.Such weight reduction features include weight-reduction recesses in thebearing support walls 75356 (not shown) and 75900 (shown in FIG. 185 )and/or the variable top and bottom profile of crank frame 7210 (shown inFIGS. 180 and 182-185 ) in various embodiments. In various embodiments,weight-reduction recesses 75900 are areas of decreased wall thicknessthat may be cast into crank frame 7210 or machined out after casting. Invarious embodiments, weight reduction features may be defined in bearingsupport walls 75356 as areas of reduced wall thickness but are notdefined by perforating bearing support walls 75356. In variousinstances, by cutting out weight-reduction recesses 75410 rather thancasting them, may be more cost effective and ensure better qualitycontrol (e.g., ensuring the integrity of bearing support walls 75356).

In various embodiments, the walls of crank frame 7210 that define stayrod through holes 72404 define raised ribs 75420 separated by recessedportions 75424. Referring now to FIG. 185 , in various embodiments,weight-reduction recesses 75900 correspond with the opposite side ofrecessed portions 75424. In the embodiment shown, a weight-reductionrecess 75900 is disposed between each bearing support wall 75356 and isdefined by a deeper portion 75904 and a transition portion 75902corresponding to each stay rod through hole 72404 to ensure the minimumwall thickness discussed herein. In various embodiments, therefore,various weight reduction features are defined in crank frame 7210between the bearing support walls 75356 and within bearing support walls75356. Further, because in various embodiments crank frame 7210 is cast,these features also reduce the material cost of the crank frame 7210.

In various embodiments, the top of crank frame 7210 includes a pluralityof lubrication ports 75422 disposed between the raised ribs 75420. Invarious embodiments, lubrication ports 75422 are centered longitudinallyand spaced transversely such that they are positioned directly over theouter race of each main bearing 75300 when mounted in the crank frame7210. The lubrication ports 75422 may be threaded to accept alubrication hose (not shown) of lubrication system 7700.

Referring now individually to FIG. 183 , a plurality of holes 75700 and75702 are formed in the side of crank frame 7210. In variousembodiments, holes 75700 are configured to receive fasteners 75314 tosecure gearbox adapter flange 75316 to crank frame 7210. In variousembodiments, holes 75702 are configured to receive studs 75315 which areused to align crank frame 7210 with gearbox adapter flange 75316 toprevent misalignment between gearbox adapter flange 75316 to crank frame7210, which might result the failure of either or both.

Referring to FIGS. 180 and 182-186 , a plurality of feet 75400 aredisposed at various positions around the base of crank frame 7210. Invarious embodiments, a pair of feet 75400 correspond to each mainbearing 75300. In various embodiments, each foot 75400 includes a pairof holes 75402 configured to receive a fastener (e.g., a stud 76402secured by a nut 76404 as shown in FIG. 190 ) that couples the foot75400 to base section 7140. As shown in FIG. 184 , each foot 75400 atthe front of crank frame 7210 corresponds to a foot 75400 at the rear ofcrank frame 7210 with a raised rib between them. However, various otherconfigurations of feet may be used in various embodiments. For example,crank frame 7210 may include more feet, fewer feet, or even no feet.FIG. 180 also includes line CM which bisects crank frame 7210 betweenraised ribs 75420.

Referring now to FIG. 181 , a cutaway side view of crank frame 7210taken along line CM from FIG. 180 is shown. FIG. 181 includes a portionof lubrication system 7700 coupled to the top of crank frame 7210. Asdiscussed herein, in various embodiments, lubrication system 7700distributes lubricant to main bearings 75300 and to crankshaft 7212.After circulating through main bearings 75300 and crankshaft 7212,lubricant exits crank frame 7210 at a plurality of drains 71908 (alsoshown in FIGS. 184 and 185 ). As shown in FIG. 181 , drains 71908 aredisposed roughly equidistant between the front and rear of crank frame7210, and roughly equidistant between main bearings 75300. As shown inFIG. 181 , drains 71908 define an exit port through the bottom of crankframe 7210 with journaling defining a slope 75500 between drain 71908and the highest portion 75502 of the interior base surface of crankframe 7210. Accordingly, if crank frame 7210 is level, lubricant willflow from various parts of crank section 7122 down through the drains71908.

Referring now to FIGS. 187-189 , various views of crankshaft 7212 areshown. FIGS. 187 and 189 relate to a first embodiment of crankshaft 7212that is labeled crankshaft 7212A. FIG. 188 relates to a secondembodiment of crankshaft 7212 that is labeled crankshaft 7212B. Asdiscussed in additional detail herein, crankshaft 7212A and crankshaft7212B include internal mechanisms for receiving and distributinglubricant and primarily differ by having different weight reductionfeatures. Referring now to FIG. 170 , a first embodiment of crankshaft7212A includes a plurality of bearing journals 76100, bearing journalcut outs 76110, crank journals 76108, crank journal radii 76112,threaded holes 76102, and outlet ports 76104. Crankshaft 7212A includesa lubrication conduit 76300 (shown in FIG. 189 ), inlet ports 76114,outlet ports 76104, and plugs (not shown) that are also components ofthe power end lubrication system.

In various embodiments, the outside diameter of the bearing journals76100 are sized to have an interference fit with the inner race of themain bearings 75300, as shown in FIG. 181 . As shown in FIG. 187 ,bearing journal cut outs 76110 are non-perforating recesses that reducethe weight of crankshaft 7212A.

Continuing with FIGS. 187-189 , crank journal radii 76112 are the radiiin the transition between the crank journal 76108 and bearing journal76100. In prior art crankshafts, these radii do not exist or are notfully formed because the position of the outside diameter of the crankjournal 76108 is close to the position of the outside diameter of thebearing journal 76100. This position is measured radially from thecentral rotation axis of the crankshafts 7212A and 7212B which isparallel to the transverse axis of power end 103. This lack of a fullcrank journal radius 76112 in the prior art generates a stressconcentration at this point and is a common failure point ofcrankshafts. The ability to form a full crank journal radius 76112 atthis point eliminates the stress concentration present in the prior artincreasing the service life of the crankshafts 7212A and 7212B.

The threaded holes 76102 receive fasteners 75310 to mount the connectingadapter 75308 to the crankshaft 7212A/7212B. There may be threaded holes76102 on one or both ends of the crankshaft 7212A/7212B depending onwhether it is known if the power end 103 will be driven from one end orboth ends. One or more of the holes 76102 may not be threaded butinstead receive locating pins 75306 (shown in FIG. 179 ) to aid in theattachment of any connecting adapters 75308.

Referring now to FIG. 188 , a view of crankshaft 7212A showinglubrication distribution bores through crankshaft 7212 is shown. Alubrication conduit 76300 formed by bores between inlet ports 76114 andoutlet ports 76104. For simplicity, only lubrication conduit 76300 isshown in FIG. 189 in order to illustrate the lubricant path. Other boresthrough crankshaft 7212A that are not a part of the lubricant conduit76300 are omitted for clarity. To fabricate the lubrication conduit76300 the intersecting bores 7303 are made diagonally from the outsidediameter of the bearing journal 76100 to the center of each crankjournal 76108. The inlet ports 76114 are at the center of the bearingjournals 76100. Inlet ports 76114 are attached to the power endlubrication system (not shown). The outlet ports 76104 are centeredaxially on each crank journal 76108 so that as lubricant is forced outof the outlet port 76104 it will lubricate the area between the crankjournal 76108 and connecting rod bearing (cap side) 73842, shown in FIG.178 .

Base Section 7140

Referring now to FIG. 190 , base section 7140 of power end 103 is shownin further detail. The embodiment of base section 7140 shown in FIG. 190includes a frame 76400, a plurality of studs 76402, a plurality of nuts76404, and a drive section support 76420. In various embodiments, frame76400 may be made from any type of structural steel and includes variousstructural components 76406 between transverse bars 76408, mount blocks76410, and threaded stud holes 76412. In various embodiments, the sizeand location of each of these components will vary based on the specificmounting needs of the particular embodiment of high pressure pump 101.In various embodiments, crosshead section 7124 and crank section 7122are secured to base section 7140 by each crosshead frame 7220 (e.g.,using base section attachment hole 74402 that receives a stud 76402 thatis secured by a nut 76404) and each foot (e.g., foot 75400) of crankframe 7210 (e.g., using holes 75402 that receive respective studs 76402that are secured by a respective nut 76404). In some embodiments,however, not every crosshead frame 7220 or each foot of crank frame 7210are secured to base section 7140. In some embodiments, some or all ofplates 7202, 7204, and 7206 may be secured to base section 7140 (e.g.,via flanges extending from the various plates) (not shown).

In various embodiments, drive section support 76420 is a saddle-shapedfeature on which drive section 7130 rests. In various embodiments, drivesection support 76420 is integral to the rest of base section 7140, butin other embodiments drive section support 76420 may be bolted and/orwelded on. In various embodiments, drive section 7130 accounts for about20% of the total weight of pump 101. If this weight is left hanging offthe side of crank section 7122, undue stress may be placed on the sideof crank frame 7210. Accordingly, drive section support 76420 isconfigured to carry the full weight of drive section 7130. In variousembodiments, drive section support 76420 includes a plurality of setscrews usable to adjust contact with drive section 7130 (e.g., to ensurea proper fit).

Assembly of Power End 103

In accordance with various embodiments discussed herein, power end 103may be assembled as follows: a crankshaft 7212 is inserted into a crankframe 7210 to form crank section 7122. A rear support plate 7200 iscoupled to the back of crank frame 7210. A plurality of crossheadassemblies 71700 are coupled to crankshaft 7212. In various embodiments,crosshead assembly 71700 is coupled to crankshaft 7212 by installingcomponents through the front of crank section 7122 and through the rear(e.g., through maintenance openings 72444). A central support plate 7202is coupled to the front of crank section 7122 (using the alignmentdowels 72452) such that the crosshead assemblies 71700 are disposedthrough crosshead ports 72420 of central support plate 7202. Crossheadsection 7124 is formed by coupling a plurality of crosshead frames 7220to central support plate 7202 (using alignment dowels 71910) such thatthe crosshead assemblies 71700 are disposed within central bores 74600of crosshead frames 7220 and pony rod clamp 7802 is disposed outside thecrosshead frames 7220 and sealed using pony rod seal housing 73800.

Washers 72406 and nuts 72408 are disposed around a first set of rods120, and nuts 72408 are tightened on one end of each of the first set ofrods 7240 such that nuts 72408 are fully engaged. The other ends of thefirst set of rods 7240 are inserted through rear support plate 7200,through crank section 7122, through central support plate 7202, andthrough the individual crosshead frames 7220. A top front support plate7204 and bottom front support plate 7206 are placed over the ends offirst set of rods 7240 protruding from crosshead frames 7220. Washers72402 and nuts 72400 are then placed over the ends of first set of rods7240 protruding from a top front support plate 7204 and bottom frontsupport plate 7206, and nuts 72400 are torqued down as discussed herein.As a result, first set of rods 7240 are in a state of tension and plates7200, 7202, 7204, and 7206 as well as crank section 7122 and crossheadsection 7124 are compressed.

Then a second set of rods 120 are inserted through top front supportplate 7204, bottom front support plate 7206, and crosshead frames 7220and torqued into threaded connect plate stay rod holes 71702 in centralsupport plate 7202 such that the second set of rods 120 are fullyengaged with central support plate 7202. A plurality of spacers 122 areinstalled (using alignment pins 7906) around the protruding ends of thesecond set of rods 120 followed by a plurality of individual connectplates 118. Washers 134 and nuts 132 are then placed over the ends ofsecond set of rods 120 protruding from individual connect plates 118 andare torqued down as discussed herein. As a result, second set of rods120 are in a state of tension and plates 7202, 7204, and 7206 as well ascrosshead section 7124 and connect section 7126 are compressed.Lubrication system 7700 is coupled to power end 103, and fluid end 100is coupled to power end 103 by coupling the various fluid end sections102 to the individual connect plates 118 and coupling plungers 290 ofthe fluid end 100 to pony rod clamp 802.

Maintenance of Power End 103

As discussed herein, in contrast to traditional power ends, like thepower end 34 shown in FIG. 3 , power end 103 employs a modular design inwhich various individual components may be removed and replaced asneeded (e.g., when a component wears out or fails). In particular,crosshead frames 7220, crosshead assemblies 71700, connect plates 118,and spacers 122 may be replaced. As discussed herein, stresses on thesecomponents that result from compressing fluid in fluid end 100 mayresult in wear and failure to these pieces. Additionally, if lubricationsystem 7700 fails (e.g., a line becomes clogged), crosshead frame 7220and/or crosshead assembly 71700 might be damaged. Accordingly, byreplacing various modular components, power end 103 may be more quicklybrought back into service by loosening nuts (e.g., nuts 132, 72400),installing a replacement component, and torqueing down nuts. Incontrast, prior power end assemblies might have required field weldingor other more labor-intensive repairs.

Thus, in accordance with various embodiments discussed herein, power end103 may be assembled as follows: a plurality of nuts 132 are disengaged;at least a portion of connector section 7126 is removed (e.g., connectplate 118, spacers 122). If connecter section 7126 was the only reasonfor maintenance, then replacement connect plates 118 or spacers 122 maybe installed and nuts 132 may be installed and torqued down as discussedherein. If a particular connect plate 118 does not need to be replaced,the fluid end section 102 that is coupled thereto does not need to bedisengaged from that particular connect plate 118. If components ofcrosshead section 7124 are to be replaced, nuts 72400 are disengaged,plates 7204 and 7206 are removed, and one or more crosshead frames 7220are removed. Repairs may be made to crosshead assembly 71700 if requiredfrom the front and/or from the rear (e.g., by removing maintenance cover7510). A replacement crosshead frame 7220 may be installed, and plates7204 and 7206 may be replaced. Nuts 72400 may then be reengaged andconnector section 7126 and second set of rods 120 may be replaced.

As used herein, “modular” means an apparatus that is comprised of aplurality of components joined together to form a complete apparatus.Such components may be removable and replaceable with like components,if needed. For example, in some embodiments of the power end 103described herein, the power end 103 comprises a plurality of crossheadframes joined together to form the crosshead section of the power end103. Each crosshead frame is removable and may be replaced with a newcrosshead frame, if needed. Likewise, in some embodiments of the fluidend 100 described herein, the fluid end 100 comprises a plurality offluid end sections 102 joined together to form the fluid end 100. Eachfluid end section 102 may be removed and replaced with a new fluid endsection 102, if needed.

In some cases, components making up the modular apparatus arenumerically related to other module components in the apparatus. Forexample, in some embodiments of the power end 103, the crosshead frames,crosshead assemblies, spacers, and connect plates are individuallyreplaceable and are related in number (e.g., for each crosshead framethere is one crosshead assembly, one connect plate, and four spacers).Similarly, in various embodiments of the fluid end 100, the fluid end100 is composed of individual fluid end sections 102, and for each fluidend section 102, there may be one housing, one fluid routing plug, oneplunger, one discharge valve, one suction valve, one discharge valveguide, and one suction valve guide, each of which is individuallyreplaceable.

In alternative embodiments, the various features described herein may beconstructed like one or more of those embodiments described in U.S.patent application Ser. No. 16/951,605, authored by Thomas et al., filedon Nov. 18, 2020, and titled “Fluid Routing Plug”; U.S. patentapplication Ser. No. 16/951,741, authored by Thomas et al., filed onNov. 18, 2020, and titled “Fluid End”; and U.S. patent application Ser.No. 16/951,844, authored by Foster et al., filed on Nov. 18, 2020, andtitled “Modular Power End”, the entire contents of which areincorporated herein by reference.

The various features and alternative details of construction of theapparatuses described herein for the practice of the present technologywill readily occur to the skilled artisan in view of the foregoingdiscussion, and it is to be understood that even though numerouscharacteristics and advantages of various embodiments of the presenttechnology have been set forth in the foregoing description, togetherwith details of the structure and function of various embodiments of thetechnology, this detailed description is illustrative only, and changesmay be made in detail, especially in matters of structure andarrangements of parts within the principles of the present technology tothe full extent indicated by the broad general meaning of the terms inwhich the appended claims are expressed. Changes may be made in theconstruction, operation and arrangement of the various parts, elements,steps and procedures described herein without departing from the spiritand scope of the invention as described in the following claims.

The invention claimed is:
 1. An apparatus comprising: a power endassembly having opposed front and rear surfaces and comprising a centralsupport plate disposed between the front and rear surfaces; a pluralityof fluid end stay rods, each of the plurality of fluid end stay rodshaving opposed first and second ends, the first end of each of theplurality of fluid end stay rods attached to the central support plateand the second end of each of the plurality of fluid end stay rodsprojecting from the front surface of the power end assembly; in whichthe first end of each of the plurality of fluid end stay rods comprisesa threaded outer surface configured to mate with a correspondingthreaded opening formed in the central support plate; a fluid endassembly attached to the second end of each of the plurality of fluidend stay rods; and a plurality of power end stay rods, each of theplurality of power end stay rods traversing the power end assembly andhaving opposed first and second ends, each of the first and second endsof the plurality of power end stay rods having a nut installed thereon.2. An apparatus comprising: a power end assembly having opposed frontand rear surfaces and comprising: a crank section comprising acrankshaft; a crosshead section offset from the crank section andcomprising a plurality of crossheads; in which the crankshaft is joinedto the plurality of crossheads by a plurality of connecting rods; and acentral support plate disposed between the crankshaft and the pluralityof crossheads such that the plurality of connecting rods extend throughcorresponding bores formed within the central support plate; and inwhich the central support plate is disposed between the crank sectionand the crosshead section; a plurality of stay rods, each of theplurality of stay rods having opposed first and second ends, the firstend of each of the plurality of stay rods attached to the centralsupport plate and the second end of each of the plurality of stay rodsprojecting from the front surface of the power end assembly; in whichthe first end of each of the plurality of stay rods comprises a threadedouter surface configured to mate with a corresponding threaded openingformed in the central support plate; and a fluid end assembly attachedto the second end of each of the plurality of stay rods; a plurality ofpower end stay rods, each of the plurality of power end stay rodstraversing the crank section, the central support plate, and thecrosshead section; and a plurality of threaded nuts, each of theplurality of threaded nuts attached to an end of each of the pluralityof power end stay rods.
 3. A method of assembling the apparatus of claim2, comprising: attaching the first end of each of the plurality of stayrods to the central support plate; and thereafter, attaching the fluidend assembly to the second end of each of the plurality of stay rods. 4.The apparatus of claim 2, in which the apparatus is situated within anambient environment, in which at least a portion of each end of each ofthe plurality of power end stay rods is exposed to the ambientenvironment.
 5. The apparatus of claim 2, in which each of the pluralityof stay rods has a first longitudinal axis; in which each of theplurality of power end stay rods has a second longitudinal axis; and inwhich the first longitudinal axis is offset from the second longitudinalaxis.
 6. The apparatus of claim 2, in which the plurality of stay rodscomprises: a plurality of upper stay rods positioned in a spacedrelationship with a plurality of lower stay rods; and in which theplurality of power end stay rods comprises: a plurality of upper powerend stay rods positioned in a spaced relationship with a plurality oflower power end stay rods; in which the plurality of upper stay rods,the plurality of lower stay rods, the plurality of upper power end stayrods and the plurality of lower power end stay rods are positioned inconsecutive rows relative to the front surface of the power endassembly, the first row comprising the plurality of upper power end stayrods, the second row comprising the plurality of upper stay rods, thethird row comprising the plurality of lower stay rods, and the fourthrow comprising the plurality of lower power end stay rods.
 7. A methodof assembling the apparatus of claim 2, comprising: installing theplurality of power end stay rods through aligned passages formed withinthe crosshead section, the central support plate, and the crank section;thereafter, attaching the plurality of threaded nuts to the end of eachof the power end stay rods and torquing the plurality of threaded nutsagainst the power end assembly; thereafter, attaching the first end ofeach of the plurality of stay rods to the central support plate; andthereafter, attaching the fluid end assembly to the second end of eachof the plurality of stay rods.
 8. The apparatus of claim 2, in which thepower end assembly further comprises: a rear support plate; and in whichthe crank section is disposed between the rear support plate and thecentral support plate; and in which the plurality of power end stay rodsalso traverse the rear support plate.
 9. The apparatus of claim 2, inwhich the apparatus is situated in an ambient environment, and in whichthe crosshead section further comprises: a plurality of crosshead framessituated in a side-by-side relationship, each crosshead frame of theplurality of crosshead frames housing a corresponding one of theplurality of crossheads; in which an outer surface of each of theplurality of crosshead frames is exposed to the ambient environment. 10.The apparatus of claim 2, in which the plurality of stay rods are in aspaced relationship with the plurality of power end stay rods.
 11. Theapparatus of claim 2, in which each of the plurality of stay rodstraverses the crosshead section, but not the crank section.
 12. Theapparatus of claim 2, in which the central support plate is ofsingle-piece construction.
 13. The apparatus of claim 2, furthercomprising: a sleeve disposed around each of the plurality of stay rodsand interposed between the fluid end assembly and the front surface ofthe power end assembly.
 14. The apparatus of claim 2, in which theapparatus is situated in an ambient environment; and in which at least aportion of the central support plate is exposed to the ambientenvironment.
 15. The apparatus of claim 2, further comprising: an upperintake manifold attached to the fluid end assembly; a lower intakemanifold attached to the fluid end assembly; and a discharge manifoldattached to the fluid end assembly.
 16. The apparatus of claim 2, inwhich the fluid end assembly comprises: a plurality of fluid endsections situated in a side-by-side and spaced relationship, each of theplurality of fluid end sections attached to at least one of theplurality of the stay rods.
 17. The apparatus of claim 16, in which eachof the plurality of fluid end sections comprises: a housing having ahorizontal bore formed therein; and a fluid routing plug installedwithin the horizontal bore.
 18. The apparatus of claim 17, in which thehousing further comprises: a beveled surface formed in a wall or wallsof the housing and surrounding the horizontal bore; and in which thefluid routing plug comprises: a beveled surface formed on an outersurface of the fluid routing plug; in which the beveled surface of thefluid routing plug engages the beveled surface of the housing.